Hydronic building systems control

ABSTRACT

Controlling heating and cooling in a conditioned space utilizes a fluid circulating in a thermally conductive structure in fluid connection with a hydronic-to-air heat exchanger and a ground heat exchanger. Air is moved past the hydronic-to-air heat exchanger, the air having fresh air supply and stale air exhaust. Sensors located throughout the conditioned space send data to a controller. User input to the controller sets the desired set point temperature and humidity. Based upon the set point temperature and humidity and sensor data, the controller sends signals to various devices to manipulate the flow of the fluid and the air in order to achieve the desired set point temperature and humidity in the conditioned space. The temperature of the fluid is kept less than the dew point at the hydronic-to-air heat exchanger and the temperature of the fluid is kept greater than the dew point at the thermally conductive structure.

CROSS-REFERENCES TO RELATED APPLICATIONS

This application is a Continuation of U.S. patent application Ser. No.16/411,695 filed May 14, 2019, which is a Continuation of U.S. patentapplication Ser. No. 16/059,342 filed Aug. 9, 2018, now U.S. Pat. No.10,330,336 issued Jun. 25, 2019, which is a Continuation of U.S. patentapplication Ser. No. 15/202,370 filed Jul. 5, 2016, now U.S. Pat. No,10,072,863 issued Sep. 11, 2018, which is a Continuation of U.S. patentapplication Ser. No, 13/969,316 filed Aug. 16, 2013, now U.S. Pat. No,9,410,752 issued Aug. 9, 2016, which claims the benefit of US.Provisional Application No. 61/684,564 filed Aug. 17, 2012, the fulldisclosures of which are incorporated herein by reference in theirentirety for all purposes.

BACKGROUND

This disclosure is related to hydronic heating and cooling applicationsand more specifically to software control systems for hydronic heatingand cooling applications.

Identification and Significance of the Problem or Opportunity—Moreenergy is consumed by buildings than any other segment of the U.S.economy, including transportation or industry, with almost 41% of totalU.S. energy consumption devoted to taking care of our nation's home andcommercial building energy needs. This is an increase from 39% in 2006,which utilized approximately 39 quadrillion Btu (quads) of energy toservice the 113 million households and 74.8 billion square feet ofcommercial floor space in the United States. Total building primaryenergy consumption in 2009 was about 48% higher than consumption in1980. Space heating, space cooling, and lighting were the dominant enduses in 2010, accounting for close to half of all energy consumed in thebuildings sector.

More than $400 billion is spent each year to power homes and commercialbuildings, consuming more than 70% of all electricity used in the U.S.and contributing to almost 40% of the nation's carbon dioxide emissions.The Energy Information Administration estimates that energy consumptionin buildings—primarily electricity and natural gas—will exceed fiftyquads in the next two decades. If the U.S. can reduce building energyuse by 20%, approximately $80B would be saved annually on energy bills,and significant reduction of greenhouse gas emissions would be realized.

Next-generation building controls have the potential to producesignificant energy savings in buildings. For example, annual energyconsumption associated with functions addressed by conventional buildingcontrols—i.e., lighting, heating, cooling, and ventilation—totals nearlyten quads, or 57% of primary energy. These ten quads broadly frame theenergy savings opportunity for building controls. Investment inenergy-efficiency R&D within the buildings sector—especially in the keyarea of advanced controls—could significantly reduce energy consumption.However, the potential to realize these savings via innovative buildingcontrols has been hampered by several market and industry barriers.

First, R&D investment in the building industry is much lower than inmany other industries. This is in part due to market fragmentation, withmany actors required to construct and operate a building (e.g.,manufacturers, designers, builders, subcontractors, suppliers, etc.).This limits the ability of the private sector to effectively coordinateresearch and reliably bring innovations to market. Moreover, buildingcontrol innovations are particularly challenging to bring to thiscost-sensitive market because their benefits are difficult toquantify—especially without independent verification of savings levels.Investment in building energy efficiency R&D by private companiesdropped 50% between 1991 and 2003.

Development of innovative and cost-effective controls is also hamperedby ownership issues of commercial and residential buildings. Buildingoccupants who are not owners have little incentive to invest inbuilding-efficiency improvements. The owners are also unwilling toupgrade to high-efficiency equipment and appliances because they do notsee the benefit of reduced utility bills, which the occupant pays. Forexample, while utilities constitute only 1% of total building expenses,they account for 30% of tenant operating expenses. Peak demand chargesaccount for 40% of commercial building electricity expenses, of which75% of these relate to lighting and Heating, Ventilation, and AirConditioning (HVAC) systems. Most commercial buildings are coolingdominated. Ground Source Heat Pumps (GHPs) can reduce peak demandcharges by operating at one-half the peak load electrical demands ofconventional equipment. When combined with hydronic high thermal massdistribution systems, GHP-centric HVAC systems have the potential toreduce tenant operating expenses over 20%. Hydronic as used herein isdefined as the use of a fluid such as water as the heat-transfer mediumin heating and cooling systems.

Prevailing design/bid/build paradigms also impede deployment of advancedcontrols, with focus on completing buildings quickly and inexpensively.Common sequential design processes make extensive use of prior designexperience, resulting in a bias against innovative approaches with lowermarket adoption. Integrated and synergistic design of building systemsis also challenged by current practices.

Finally, a central issue with installing controls to implement energysavings measures is that energy expenditures account for a small(approximately 1%) proportion of total annual building expenditures.Investment in core business activities often competes withenergy-efficiency investments such as advanced controls. Buildingowners/operators must have very high levels of confidence thatinvestments in building controls will have a quick payback for thoseinvestments to prove attractive. The innovation disclosed hereindelivers the technology that will provide that high level of confidence.

Advanced, low-cost, “smart” building controls have the technicalpotential to reduce U.S. commercial building HVAC and lighting energyconsumption by about one quad of primary energy annually, or roughly 6%of current total use. In addition, many offer significant peak-demandreduction potential. But as stated above, advanced building controlsface first-cost and several non-economic barriers to realizing greatermarket penetration. The U.S. Department of Energy Building TechnologiesProgram understands these unique technology and industry barriers todeveloping innovative technologies, and has requested high-risk,high-reward innovative research focused on technology that has thepotential to contribute to a 50% reduction in energy demand byresidential and commercial buildings at less than the cost of the energysaved (800 trillion Btu's in annual savings by 2020 and 3,000 trillionBtu's in annual savings by 2030).

As part of that “50% reduction” effort, the Department of Energy (DOE)is striving to develop and demonstrate “crosscutting, whole buildingtechnologies such as sensors and controls. These efforts support the netzero energy buildings goal not only by reducing building energy needs,but also by developing design methods and operating strategies whichseamlessly incorporate solar and other renewable technologies intocommercial buildings.”

Integrated hydronic heating and cooling applications have the potentialto reduce the residential and commercial building energy use by 50%while increasing occupant comfort, safety, and indoor environmentalquality at substantially less cost than the energy saved.

The Hydronic Building Systems Control (HBSC) described in thisdisclosure is a low-cost standards-compliant software-based control thatintegrates traditional and renewable hydronic system components forbuilding heating, cooling, and hot water. HBSC addresses knowntechnology gaps with a software solution, and produces a controlsrequirement specification that can be hosted on commodity hardware suchas that developed for the smart phone market.

HBSC also addresses shortcomings of commonly used HVAC systems byremoving barriers to market adoption of hydronic heating and coolingsystems. Widespread use of forced air systems contributes to highhealthcare costs and decreased occupant productivity caused by poorIndoor Environmental Quality (IEQ) and thermal comfort, while increasingvulnerability to terrorist attack with potential negative impact onpublic welfare and national security. Current hydronic systemtechnologies, while highly energy efficient, struggle in the marketplacedue to system cost, controller complexity, and retrofit difficulty. HBSCtechnology has the ability to overcome problems with forced air systemsproviding heating, cooling, and ventilation.

The American Society of Heating Refrigeration and Air ConditioningEngineers (ASHRAE) and international standards organizations mandate theuse of mechanical ventilation to provide fresh air in tight buildings.For higher system energy efficiency, heat recovery is combined with themechanical ventilation using an energy transfer and ventilation device.The heat exchange and ventilation is usually achieved with an air-to-airheat exchanger with one or more built-in fans, commonly known as a HeatRecovery Ventilator (HRV) or Energy Recovery Ventilator (ERV). Inclimates where heating is more prevalent than air conditioning, an HRVis used. In cooling climates, an ERV is recommended. In hot humidclimates, air conditioning and/or dehumidification equipment are used inconjunction with ERVs or HRVs to enhance user comfort and indoorclimate.

Within a HRV, contaminated exhaust air and fresh outside air passthrough the heat recovery core in separate passages that prevent aircontamination or mixture. The fresh outside air then absorbs the heatand warms up, and is distributed at a more comfortable temperature tothe various rooms by the ventilation system. An HRV can help makemechanical ventilation more cost effective by reclaiming energy fromexhaust airflows. HRVs use heat exchangers to heat or cool incomingfresh air, recapturing 60% to 80% of the conditioned temperatures thatwould otherwise be lost. Conventional fan and vent assemblies forbathrooms and kitchens, often required by building code standards forventilation, may allow significant energy losses. An HRV system canincorporate small, separately switched booster fans in these rooms tocontrol moisture or heat generated by activities like showering orcooking. Odors and pollutants can quickly be removed, but energy used tocondition the air is recycled in the heat exchanger.

ERVs exchange moisture between the exhaust and fresh air streams. ERVsare especially recommended in climates where cooling loads place strongdemands on HVAC systems. In some cases, ERVs may be suitable in climateswith very cold winters. If indoor relative humidity tends to be too low,what available moisture there is in the indoor exhaust air stream istransferred to incoming outdoor air. However, ERVs are notdehumidifiers. While the ERV transfers moisture from the humid airstream (incoming outdoor air in the summer) to the exhaust air stream,the desiccant wheels used in many ERVs become saturated fairly quicklyand the moisture transfer mechanism becomes less effective withsuccessive hot, humid periods. Mechanical vapor compressionrefrigeration equipment, known as air conditioners, is the most commonapproach utilized to reduce humidity while cooling.

Refrigeration air conditioning equipment usually reduces the humidity ofthe air processed by the system. The process is highly effective incooling to reduce sensible and latent heat contained in the air.Sensible heat is the energy exchanged by a thermodynamic system that hasas its sole effect a change of temperature. Latent heat is the quantityof heat absorbed or released by a substance undergoing a change ofstate, such as ice changing to water or water to steam, at constanttemperature and atmospheric pressure. A forced-air cooling system hasthe ability to remove sensible heat (cooling the air) and remove latentheat (through dehumidification which removes heat contained in the watervapor in the air stream). The dew point is the temperature below whichthe water vapor in a volume of humid air at a given constant barometricpressure will condense into liquid water at the same rate at which itevaporates. The relatively cold (below the dew point) evaporator coilcondenses water vapor from the processed air (much like an ice-colddrink will condense water on the outside of a glass), sending the waterto a drain and removing water vapor from the cooled space and loweringthe relative humidity. Since humans perspire to provide natural coolingby the evaporation of perspiration from the skin, drier air (up to apoint) improves the comfort provided. Humans are most comfortable when40% to 50% relative humidity is maintained in the occupied space.

A specific type of air conditioner that is used only for dehumidifyingis called a dehumidifier. A dehumidifier is different from a regular airconditioner in that both the evaporator and condenser coils are placedin the same air path, and the entire unit is placed in the environmentthat is intended to be conditioned (in this case dehumidified), ratherthan requiring an external condenser coil. Having the condenser coil inthe same air path as the evaporator coil produces warm, dehumidifiedair. The evaporator (cold) coil is placed first in the air path,dehumidifying the air exactly as a regular air conditioner does. The airnext passes over the condenser coil re-warming the now dehumidified air.Note that the terms “condenser coil” and “evaporator coil” do not referto the behavior of water in the air as it passes over each coil; insteadthey refer to the phases of the refrigeration cycle. Having thecondenser coil in the main air path rather than in a separate, outdoorair path (as in a regular air conditioner) results in twoconsequences—the output air is warm rather than cold, and the unit isable to be placed anywhere in the environment to be conditioned, withouta need for an external condenser.

Unlike a regular air conditioner, a dehumidifier will actually heat aroom just as an electric heater that draws the same amount of power asthe dehumidifier. A traditional air conditioner transfers energy out ofthe room by means of the condenser coil, which is outside the room. Inthis thermodynamic system, the room is the system and energy istransferred out of the system. Conversely with a dehumidifier, no energyis transferred out of the thermodynamic system because the dehumidifieris entirely inside the room. The power consumed by the dehumidifier isenergy that is input into the thermodynamic system and remains in theroom as heat energy.

Air-conditioning systems using cooling towers can promote the growth andspread of microorganisms, such as Legionella pneumophila, the infectiousagent responsible for Legionnaires' disease, or thermophilicactinomycetes. Conversely, air conditioning, including filtration,humidification, cooling, disinfection, etc., can be used to provide aclean, safe, hypoallergenic atmosphere in environments where anappropriate atmosphere is critical to occupant safety and well-being.Air conditioning can have a negative effect by drying out the aircausing dry skin and negatively affecting sufferers of allergies andasthma. Air conditioning can also be used for dehumidification, as watervapor condenses on the air coil during cooling.

Specific issues associated with forced air HVAC systems include:

-   -   1. Poor Energy Performance Due To Distribution Ductwork—Poorly        installed forced air residential HVAC systems often use twice        the energy of a properly installed system. Duct leakage in        commercial buildings accounts for 0.3 quads of annual energy        consumption. In a study involving residences in Fresno, Calif.,        93% of the homes had duct leakage greater than 150 cubic feet        per minute. A recent audit of certified air conditioning        contractors by Xcel Energy for a high efficiency rebate program        in Colorado found that in 46% of the retrofit installations        conducted in 2011, neither the ductwork nor the equipment was        installed correctly.    -   2. Poor IEQ and Thermal Comfort—Prior research shows a        correlation between employee productivity, IEQ, and thermal        comfort. The costs attributable to these indoor climate        conditions have a greater economic impact than all building        operations and energy expenses combined. The dominance of worker        salaries as a percentage of office building expenses is        staggering, accounting for approximately 80% of expenditures in        a small office building. Increasing employee productivity 2%        would offset all building operations and energy expenses        combined. The healthcare and legal costs associated with poor        IEQ are equally formidable. For example, Legionnaire's disease        can occur from the airborne dispersal of Legionella bacteria        from improperly maintained cooling towers, humidifiers, and        evaporative condensers. Most building owners do not acknowledge        that forced air HVAC systems are causal agents to poor IEQ        resulting in higher absenteeism or poor health.    -   3. Vulnerability to Terrorist Attack—Commercial building owners        are ignorant of the terrorist risk inherent with large forced        air systems. Ground-mounted HVAC equipment and the related        forced air distribution systems which return air from any one        zone to the entire building ventilation system are particularly        vulnerable. Due to the air volume required to heat, cool, and        ventilate, a typical 100 ton rated Variable Air Volume (VAV)        system weighs over twenty tons and requires 5,000 cubic feet of        space. A 100,000 square foot building requires four of these        units. In many cases the size and weight requirements force a        designer to place the units at ground level. By introducing a        chemical, biological, radioactive, or nuclear agent into these        systems, a terrorist could inflict mass human casualties and        great psychological damage.

Although hydronic systems offer solutions to these shortcomings, theybring with them a unique set of adoption barriers, including:

-   -   1. Market Bias—While HVAC system designers have a bias toward        vapor compression technology, the highest system energy        efficiency is possible with the direct use of heated or cooled        fluids in a hydronic distribution system (radiant floor, radiant        ceiling panels, chilled beams, or hydronic fan coils). Passive        cooling using chilled fluid from a Ground Source Heat Exchanger        (GHEX), and passive heating using process heat or solar fluid        provides the highest system energy efficiency. The system design        is straightforward, and the heat transfer can be accomplished        with a low energy circulator, without the need for a boiler,        chiller, or GHP. However, a barrier to adoption is the lack of a        commercial control appropriate for this application.    -   2. Perceived High First Cost—High mass radiant floor systems are        perceived to have a higher first cost than ducted air systems.        HVAC systems designers in the U.S. prefer forced air systems        over hydronic systems, though most will acknowledge that radiant        floor heating systems are more comfortable with improved IEQ to        the forced-air alternative. Designers incorrectly assume these        technologies are incompatible. Hydronic distribution used in        conjunction with hydronic fan coils is a viable compromise,        particularly with Water-to-Water (W-W) GHPs providing both hot        and chilled water. An in-floor high mass radiant heating and        cooling system—installed at a lower cost than a ducted air        system—would be market disrupting.    -   3. Poor Hydronic Control Outcomes—Customers lack confidence in        advanced control capabilities and the energy savings benefits of        integrated renewable energy equipment, such as GHPs, for the        following reasons:    -   a. Most conventional off-the-shelf controls are functional for        one device using a few sensors. With few exceptions, such as        set-back capabilities, they do not provide optimal system energy        efficiency. Residential examples include separate controls for        the furnace, hot water and HRV/ERV, with more pronounced energy        losses and thermal discomfort issues in large commercial        buildings which have even less zoning functionality.    -   b. Enterprise Direct Digital Controls (DDCs) are expensive to        install, program and maintain. Soft costs for design,        implementation, commissioning, and maintenance are substantial,        often eliminating any value for controls investment. Enterprise        controls may provide interoperability, yet usually do not        provide higher system energy efficiency. Besides the first cost        of these controls, this lack of proven performance represents        the largest market barrier. DDC is complicated, proprietary and        owners often feel “held hostage” by controls companies. The high        soft costs associated with these controls reduce building        commissioning rates to less than 5% for new construction and        0.03% of existing buildings.    -   c. Lowest Common Denominator Control Solutions—The HVAC industry        is segmented by product. Manufacturers, suppliers, and        installers are aligned to these product lines. The end result is        serial control of disparate equipment with minimal consideration        or expertise applied to system energy efficiency. Design        professionals, builders, and HVAC contractors will require a        baseline system architecture which is affordable, easy to        implement, and provides seamless interoperability between legacy        equipment and emerging technology.    -   d. Inadequate controls and equipment efficiency ratings based on        steady state test conditions have created distrust by building        owners toward control and equipment manufacturers who have        failed to deliver on efficiency claims. Equipment efficiency        ratings for heating (Coefficient Of Performance, COP) and        cooling (Seasonal/Energy Efficiency Ratings, SEER/EER) published        by the Air Conditioning and Heating Institute (ARI) are not        substantial for predicting actual system performance. The ARI        metrics are based on steady state moderate test conditions        without consideration for overall system energy efficiency        (Seasonal Performance Factor, SPF) affected by seasonal        temperature extremes, partial load conditions, intermittent        operation and HVAC distribution efficiency.    -   e. Hydronic distribution systems are more efficient than forced        air systems. Yet commercial controls in the U.S. for hydronic        applications are limited. These systems may incorporate space        heating and cooling via a radiant floor, radiant ceiling, or        distributed hydronic fan coils. In all of these distribution        methods, the highest system energy efficiency gains are possible        by controlling the operation of the heating/cooling equipment        along with the supply temperature.    -   f. W-W ground source heat pumps are more efficient with greater        functionality than boilers, yet the available GHP hydronic        controls use boiler control logic. Within the U.S., the majority        of W-W ground source heat pumps utilize a single stage        compressor and do not require multi-stage controls. However,        when a W-W GHP is equipped with a two-stage compressor, the        typical control is single stage.    -   g. Water-to-Air (W-A) GHPs are more efficient with greater        functionality than furnaces with direct exchange cooling or air        source heat pumps, yet the available controls are often modified        furnace/air conditioner thermostats with three levels of        heating, two cooling, and a fan mode. Source circulator control        as provided by the GHP manufacturer is typically a binary relay.        Since the source circulators are usually contained in one “flow        center,” this on-off functionality activates all of the source        side circulator pumps providing sufficient flow for the rated        maximum capacity of the GHP. In a residential application        utilizing a GHP equipped with a two-stage compressor, the GHP        operates at second stage less that 20% of the heating/cooling        season. One pump in a typical two pump flow center uses 500        watts of power. If the heat pump is rated at 6 tons, two pumps        are used. Yet at partial load conditions, only one pump is        required. By reducing the source flow when the GHP is at partial        load conditions, the system energy efficiency is increased        without changing the GHP's component efficiency. The excessive        energy use of these circulators under partial load conditions is        not accounted for in GHP ARI ratings. In typical applications,        the circulators are fixed speed. Unless the GHP or controls        manufacturer provides energy efficient circulator control, the        overall highest system energy efficiency—which includes the        energy consumption of source side circulator pumps—is not        optimum. If the manufacturer does not provide relays for        multiple pumps, multiple speed pumps, or variable speed pumps        control, installing contractors install the flow center with all        pumps active regardless of actual flow requirements under        partial load conditions. These limitations cause the GHPs to        underperform with respect to advertised efficiencies derived in        steady state testing. Recently, dedicated variable speed        controllers are offered on board heat pumps equipped with        variable speed compressors. Source side pump control is not        typically available for enterprise control of multiple heat        pumps. Attaining the highest system energy efficiency determines        the operation of the circulator pumps. An industry acceptable        flow rate for a ground or water source heat pump is 3 gallons        per minute per ton of actual output. A heat pump incorporating a        multi-stage or variable speed compressor does not require flow        at the rated capacity, rather a flow rate which meets the actual        capacity. The required flow may also be varied based on the        entering water temperature to the heat pump. However, existing        logic boards with the GHPs assume that source water temperature        cannot be varied, so available controls do not account for water        temperature variances when optimizing system energy efficiency.    -   4. Lost Cost Reduction Opportunities Are Missed Without        Synergistic Design    -   a. High mass radiant floor heating infrastructure can use the        same distribution medium for cooling. Due to a lack of capable        and cost effective controls for chilled beams and Radiant Floor        Cooling (RFC), building owners typically install two complete        distribution systems—high mass radiant hydronic heating and        ducted air system for cooling and ventilation. Radiant cooling        systems use 42% less energy than comparable VAV systems (see        Table 1 below).

TABLE 1 Peak HVAC Energy Consumption Comparison, VAV versus RadiantCooling Item % Power in VAV % Power in Radiant Cooling Fan And Motor37.5% 1.5% Load From Lights 18.8% 9.4% Air Transport Load  9.3% 1.9%Other Loads 34.4% 34.4% Pumps — 1.5% Total  100% 57.7%

-   -   The savings illustrated above result from the efficiencies        created by hydronic distribution, increased effectiveness of        radiant cooling to remove infrared heat gains from direct solar        and lighting sources, and reduced air transport loads. These        savings are based on using traditional chillers operating at        less than one-half the efficiency of W-W GHPs. GHPs are ideal to        replace boilers in Radiant Floor Heating (RFH) applications due        to the lower supply temperatures required with radiant hydronic        distribution. Building owners often replace inefficient boilers        with condensing boilers as the first costs of GHPs do not        justify an investment for heating only operations. Yet GHP        equipment combined with radiant cooling architectures would        decrease energy use far more than the 42.3% savings predicted        above.    -   b. Hydronic heating and cooling systems create an opportunity to        incorporate Dedicated

Outdoor Air System (DOAS) or Demand Controlled Ventilation (DCV) toimprove system energy efficiency, IEQ, and occupant comfort. When forcedair systems are designed for ventilation and latent heat extractiononly, and not the building heating and cooling sensible loads, therequired air velocity and volume are greatly reduced. DOAS is a type ofHVAC system that consists of two parallel systems: a dedicated outdoorair ventilation system that handles latent loads and a parallel systemto handle sensible loads. DCV systems modulate outdoor intake based oncarbon dioxide levels. These systems have a simple payback period of 2-5years and the national energy savings potential of 0.3 quads.

-   -   c. Solar thermal array capacity is constrained by storage        capacity. Solar thermal tanks require a higher first cost        investment than solar thermal collectors. Reducing the        requirement to install storage tanks to match the solar array        could reduce the first cost of solar thermal arrays by 50%,        while eliminating the maintenance and replacement costs for over        sizing storage to meet array demands. A ground source heat        exchanger is ideal to handle this excess capacity, yet GHP        contractors are not familiar with design criteria for this        hybrid system and lack the controls to implement a design.

SUMMARY

This Summary is provided to introduce in a simplified form a selectionof concepts that are further described below in the DetailedDescription. This Summary is not intended to identify key or essentialfeatures of the claimed subject matter, nor is it intended to be used tolimit the scope of the claimed subject matter.

The Hydronic Building Systems Control is a temperature and humiditycontrol apparatus for air and temperature variable fluid in an airspace, comprising a thermally-conductive structure, such as a buildingfloor, wall, or ceiling; hydronic coil-to-air heat exchanger; a sourceof liquid coolant at a temperature below or above the temperature of theair space; controllable means for applying a temperature variable liquidat a temperature higher than the dew point of the air space to thethermally-conductive structure and for applying a temperature variableliquid coolant at a temperature lower than the dew point to the hydroniccoil-to-air heat exchanger; means for sensing at least the airtemperature in the air space, a relative humidity of the air space, atemperature of the thermally-conductive structure, and liquid sourcetemperatures; a controller coupled to the sensing means and to thecontrollable means.

Proposed Innovation Objectives—The Detailed Description below describesHBSC which addresses barriers facing well-integrated hydronic systemsolutions and increases the adoption of technologies that can surpassthe energy performance of conventional forced air distribution systems,while providing superior health, safety, and comfort benefits.Objectives of HBSC include, but are not limited to:

-   -   1. Delivery at Speed and Scale—Commercialize a product in less        than two years at a price which drives rapid market adoption.    -   2. Interoperability—Design interoperable solutions that improve        the ease and likelihood of system energy efficiency retrofits.    -   3. Accelerate the implementation of affordable hydronic        distribution systems.    -   4. Increase the market acceptance for ground source heat pumps.    -   5. Lower the cost and improve the solar fraction of solar        thermal systems.    -   6. Create a control requiring minimal or no user input for        optimum operation with high reliability and proven energy        savings, which minimizes the soft costs attributable to        installation, commissioning, and maintenance.    -   7. Drive the early adoption of high impact emerging        technologies, which will improve the efficiency of integrated        hydronic systems, including high thermal conductivity        nanofluids, multifunction sensors, and self-optimizing        algorithms.

Public Benefits—HBSC provides the following public benefits:

-   -   1. HBSC will ease the financial burden and accelerate the        adoption of system energy efficiency improvements reducing        environmental impact and global energy use for building heating,        cooling, and hot water.    -   2. Reduce the soft costs attributable to installation,        commissioning, and maintenance through self-optimization and        intuitive graphical user interface.    -   3. Lower operating costs with a reliable control which builds        owner confidence creating wider acceptance of hydronic        distribution and enterprise systems.    -   4. Improve IEQ and thermal comfort which increases occupant        productivity and health, and reduces absenteeism and associated        health care costs.    -   5. Eliminate the potential vulnerabilities associated with        exposed air handling equipment in commercial buildings with        hydronic distribution systems which decouple heating and cooling        from ventilation air flows.    -   6. Increase market adoption of GHP and solar thermal        technologies.    -   7. Accelerate the adoption of emerging technologies which will        improve energy efficiency, such as enhanced thermal conductivity        nanofluids, multifunction sensors, and self-optimizing        algorithms for optimal system energy efficiency.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 is a process model diagram that shows the requisite controlfunctionality and critical parameters of an embodiment of HBSC.

FIG. 2 shows a bar graph of HBSC energy savings potential compared to abaseline HVAC system.

FIG. 3 shows the technology gaps addressed by HBSC.

FIG. 4 shows a client-server computing architecture applicable to HBSC.

FIG. 5 shows a HBSC device serving as an application controller in anenterprise building automation system.

FIG. 6 shows a comparison of temperature levels for a radiator systemwith no lag time and ten minutes lag time.

FIG. 7 shows the predicted radiant floor cooling efficiency for U.S.climate zones.

FIG. 8 shows a GHP parallel piping design versus a serial boilerconnection to a hydronic system.

FIG. 9 shows the boundaries for optimizing the demand and source systemsfor a typical GHP.

To assist in the understanding of the present disclosure the followingTable Of Components and associated numbering found in the drawings isprovided below.

Table of Components Component # User Interface 2 Communications Module 4Sensor Inputs 6 Mixed Radiant Supply Fluid 8 Conditioned Space 10Microprocessor Controller 12 Radiant Mixing Device 14Thermally-Conductive Structure 16 Stale Exhaust Air 18 Air Duct Exhaust20 Devices Controller 22 Conditioned Air 24 Air Duct Intake 26 FreshIntake Air 28 Fresh Air Fan 30 Energy Transfer and Ventilation Device 32Exhaust Air Fan 34 Fresh Air Supply 36 Hydronic Supply Fluid 38 HydronicReturn Fluid 40 Hydronic Coil-to-Air Heat Exchanger 42 Thermal StorageTemperature Sensor One 44 Thermal Storage One 46 Hydronic Coil ReturnFluid 48 Hydronic Coil Supply Fluid 50 Hydronic Load Circulator 52Hydronic-to-Air Circulator 54 Source 3-Way Control Valves One 56 Source3-Way Control Valves Two 58 Source Side Circulator One 60 Source SideCirculator Two 62 Ground Heat Exchanger One 64 Ground Heat Exchanger Two66 Process Heat Exchanger 68 Load Circulator 70 Heat Pump 72 Bypass3-Way Control Valves 74 Source Heat Exchanger 76 Thermal Storage Source3-Way Control Valves 78 Thermal Storage Two 80 Thermal StorageTemperature Sensor Two 82 Thermal Load 3-Way Control Valves 84 SourceMixing Device One 86 Source Mixing Device Two 88 Process Heat Circulator90 Client Server Architecture 400 Client 402 Client 404 Client 406Server 408

DETAILED DESCRIPTION

The invention may be implemented as a computer process, a computingsystem or as an article of manufacture such as a computer programproduct. The computer program product may be a computer storage mediumreadable by a computer system and encoding a computer program ofinstructions for executing a computer process. The computer programproduct may also be a propagated signal on a carrier readable by acomputing system and encoding a computer program of instructions forexecuting a computer process.

Technical Approach—Described in detail below is a low coststandards-based integrated Hydronic Building Systems Control. Oneembodiment is based on the BACnet protocol and HBSC algorithms arehosted on commodity hardware developed for the smart phone market. HBSCprovides interoperability between legacy and new HVAC equipment, and isdesigned using a process model which incorporates hydronic fan coils andhigh mass radiant floor hydronic heating and cooling incorporatingground source heat pumps source circulator control, process heat andsolar thermal sources, ground heat exchanger passive cooling, and dewpoint tracking for high mass radiant cooling applications.

Referring now to the Figures, like reference numerals and names refer tostructurally and/or functionally similar elements thereof, and ifobjects depicted in the figures that are covered by another object, aswell as the tag line for the element number thereto, may be shown indashed lines. FIG. 1 is a process model diagram that shows the requisitecontrol functionality and critical parameters of an embodiment of HBSC.To simplify the control optimization strategy, HBSC utilizes theexplicit process model shown in FIG. 1 to determine critical parameters.Since this approach is vendor and technology agnostic, HBSC providesdirect control and interoperability through modulation of single ormulti-stage legacy equipment while providing a path to accommodateemerging Variable Speed (VS) devices with onboard optimization. HBSCuses a model-based design with minimal sensed feedback for reduced cost,and operates more rapidly than direct search method approaches, whichperturb physical process variables to reactively optimize systemperformance. Notwithstanding the above, one skilled in the art willrecognize that individual components shown in FIG. 1 can be arranged inmany different configurations, and that specific components may bedifferent types of devices selected to meet specific requirements for agiven structure. FIG. 1 should not be viewed in a limiting way, but asan exemplary embodiment of the features and functions as set out in theclaims that follow.

HBSC Innovation Description and Sequence of Controls—Referring now toFIG. 1, HBSC is based on a model consisting of a combination of analogdevices using a circulating fluid to heat or cool a Conditioned Space10, such as a room in a home or an office in a building, or multipleconditioned spaces, in a Thermally-Conductive Structure 16, such asradiant floors, walls, and ceilings, or chilled beams.

The fluid may be used to transfer energy by circulating the fluidthrough a Hydronic Coil-to-Air Heat Exchanger 42 in combination with adevice which moves air through Hydronic Coil-to-Air Heat Exchanger 42.The fluid may be water, propylene glycol, ethanol, methanol, or anyother suitable fluid that is typically non-corrosive. In anotherembodiment, Hydronic Coil-to-Air Heat Exchanger 42 may be adehumidifier, and air conditioning unit (mechanical vapor compressionrefrigeration equipment), an absorption chiller, or a heat recoveryventilator. The air moving device may be a fan, or Energy Transfer andVentilation Device 32 such as an ERV, HRV, water-to-air heat pump,water-to-water heat pump, air-to-water heat pump, air conditioner, ordehumidifier.

Energy Transfer and Ventilation Device 32 uses two or more fans, such asFresh Air Fan 30 and Exhaust Air Fan 34, to bring Fresh Air Supply 36into Conditioned Space 10 while removing Stale Exhaust Air 18. Typicalimplementations utilize ventilation comprising Air Duct Intake 26 andAir Duct Exhaust 20. In this process, Energy Transfer and VentilationDevice 32 exchanges energy between the air flows (Fresh Air Supply 36and Stale Exhaust Air 18), which includes water vapor in the air,causing a change in humidity. The air flow into the conditioned space isConditioned Air 24 which differs from outside air based on interactionwith Energy Transfer and Ventilation Device 32. The entering fluid toHydronic Coil-to-Air Heat Exchanger 42 is Hydronic Coil Supply Fluid 50.The leaving fluid is Hydronic Coil Return Fluid 48. Hydronic Coil SupplyFluid 50 is pumped from Thermal Storage One 46 with Hydronic Coil-to-AirCirculator 54. The temperature of the fluid in Thermal Storage One 46(typically a chilled fluid storage tank) is sensed by Thermal StorageTemperature Sensor One 44. The temperature of the fluid in ThermalStorage Two 80 (typically a heating fluid storage tank) is sensed byThermal Storage Temperature Sensor Two 82.

When Hydronic Coil Supply Fluid 50 entering Hydronic Coil-to-Air HeatExchanger 42 is sufficiently colder than the dew point of Fresh IntakeAir 28, water will condense on Hydronic Coil-to-Air Heat Exchanger 42causing Conditioned Air 24 to be dehumidified.

The fluid in Thermal Storage One 46 (typically cold) or Thermal StorageTwo 80 (typically hot) may be used to transfer energy throughThermally-Conductive Structure 16. Typical structures utilize low orhigh mass mediums in which tubing is mounted or embedded. Applicationsinclude radiant floor, walls and ceilings, or chilled beams. Thetemperature of Mixed Radiant Supply Fluid 8 is controlled with RadiantMixing Device 14 by modulating the mixed flow of Hydronic Supply Fluid38 with Hydronic Return Fluid 40. Hydronic Supply Fluid 38 is pumped byHydronic Load Circulator 52 from Thermal Storage One 46 or ThermalStorage Two 80 based on the position of the Thermal Load 3-Way ControlValves 84. In cooling mode, the Mixed Radiant Supply Fluid 8 iscirculated at a temperature above dew point to prevent condensation inThermally-Conductive Structure 16. Chilled fluid below dew pointcontained in Thermal Storage One 46, and used to dehumidify air inHydronic Coil-to-Air Heat Exchanger 42, is mixed to a temperature abovedew point to circulate in Thermally-Conductive Structure 16.

The source of chilling or heating for the fluids contained in ThermalStorage One 46 and Thermal Storage Two 80 may be active or passive.Active heating and chilling is provided from Heat Pump 72, or an activesource containing Process Heat Exchanger 68 (typically a boiler,chiller, solar thermal array, combined heat and power unit (CHP or“cogeneration”), or an absorption chiller). Passive heating and chillingis provided from an open or closed loop Ground Heat Exchanger One 64 andGround Heat Exchanger Two 66 or Process Heat Exchanger 68 for waste heator cooling.

An open loop ground heat exchanger uses ground water directly as aheating or cooling medium, extracting and then discharging water to theground. A closed loop ground heat exchanger, as depicted at Ground HeatExchanger One 64 and Ground Heat Exchanger Two 66 utilizes pipingembedded in the ground or surface water through whichthermally-conductive fluid is circulated.

One embodiment utilizes a ground source heat pump, such as Heat Pump 72,for active chilling or heating Thermal Storage One 46 or Thermal StorageTwo 80. Another embodiment utilizes an air source heat pump (not shown)without a requirement for a Ground Heat Exchanger One 64 and Ground HeatExchanger Two 66. In chilling operation, Heat Pump 72 cools with ThermalStorage Source 3-Way Control Valves 78 directed to Thermal Storage One46. In heating operation, Heat Pump 72 heats with Thermal Storage Source3-Way Control Valves 78 directed to Thermal Storage Two 80. LoadCirculator 70 moves fluid from Thermal Storage One 46 and ThermalStorage Two 80 through the load side heat exchanger contained withinHeat Pump 72.

Heat Pump 72 may operate using an open loop or closed loop ground heatexchanger. In one embodiment, as shown in FIG. 1, Heat Pump 72 activelyheats/chills using an electric vapor compression process with a closedloop ground heat exchanger comprised of Ground Heat Exchanger One 64 andGround Heat Exchanger Two 66. This type of heat exchanger is known inthe industry as the “source side” heat exchanger. While typical groundsource heat pumps use one closed loop ground heat exchanger, the sourceside embodiment shown in FIG. 1 may use all or part of the ground heatexchanger, with and without utilizing heating or chilling from ProcessHeat Exchanger 68. The amount of flow through Ground Heat Exchanger One64 versus Process Heat Exchanger 68 is a function of the position ofSource 3-Way Control Valves One 56. The flow through Ground HeatExchanger Two 66 is a function of the position of Source 3-Way ControlValves Two 58. Flow through Ground Heat Exchanger One 64 and Ground HeatExchanger Two 66 is delivered by Source Side Circulator One 60, SourceSide Circulator Two 62, and Process Heat Circulator 90. The fluid mixingbetween Ground Heat Exchanger One 64 and Ground Heat Exchanger Two 66and Process Heat Exchanger 68 is the function of Source Mixing DeviceOne 86 and Source Mixing Device Two 88.

Attaining the highest system energy efficiency determines the operationof the circulator pumps contained in Source Side Circulator One 60 andSource Side Circulator Two 62. At maximum capacity operation andutilization of Ground Heat Exchanger One 64 and Ground Heat ExchangerTwo 66, all pumps in the Source Side Circulator One 60 and Source SideCirculator Two 62 are activated when Heat Pump 72 turns on. When HeatPump 72 is equipped with a two-stage compressor, logic within theMicroprocessor Controller 12 activates relays contained within DevicesController 22 to affect operation of the circulator pumps contained inSource Side Circulator One 60 and Source Side Circulator Two 62. Formultiple fixed speed pumps, a relay for each pump is activated toprovide sufficient flow rate to Heat Pump 72 based on MicroprocessorController 12 data. Factors affecting the source side required flow forHeat Pump 72 performance include entering water temperature from SensorInputs 6, the compressor output and heating or cooling mode demanded byMicroprocessor Controller 12, and calculated performance data providedby the manufacturer and known to Microprocessor Controller 12. Formultiple speed and variable speed pumps contained in Source SideCirculator One 60 and Source Side Circulator Two 62, digital output isprovided by Microprocessor Controller 12 to one or both Source SideCirculator One 60 and Source Side Circulator Two 62 to meet requiredsource side flow rate as calculated by Microprocessor Controller 12 tooptimize system energy efficiency. One embodiment is a 0-10 volt inputsignal corresponding to 0-100% output pump capacity. When Ground HeatExchanger One 64 and Ground Heat Exchanger Two 66 are utilized in splitoperation, as one for heating and one for cooling, MicroprocessorController 12 will activate the respective Source Side Circulator One 60and Source Side Circulator Two 62 at the pump capacity to meet therequired source side flow rate for Heat Pump 72 to meet capacity demand.

For passive heating and cooling, Thermal Storage One 46 and ThermalStorage Two 80 are heated or cooled without engaging Heat Pump 72operation. Ground Heat Exchanger One 64 and Ground Heat Exchanger Two 66and Process Heat Exchanger 68 fluids bypass the Heat Pump 72. Thesefluids may be circulated directly into Thermal Storage One 46 or ThermalStorage Two 80, or transfer energy through Source Heat Exchanger 76 asshown in the embodiment of FIG. 1. Typical ground heat exchanger fluidsare at low grade temperatures, so direct use in cooling is anappropriate application. Bypass 3-Way Control Valves 74 enable directuse of source side heat exchanger fluids bypassing Heat Pump 72. LoadCirculator 70 affects flow between Thermal Storage One 46 or ThermalStorage Two 80 and Source Heat Exchanger 76 based on the position ofThermal Storage Source 3-Way Control Valves 78. When Source HeatExchanger 76 is utilized, the Source Side Circulator One 60 and SourceSide Circulator Two 62 or Process Heat Circulator 90 must also beactivated to establish heat transfer across Source Heat Exchanger 76.

The proposed innovation is a control for a hydronic building system forspace cooling and heating. The control system for controlling a hydronicbuilding system for space cooling and heating consists of at least oneof a User Interface 2; Communications Module 4; Sensor Inputs 6 forsensing temperature, atmospheric pressure, humidity, and velocity;Microprocessor Controller 12; and Devices Controller 22. These devicescan operate as separate modules or integrated components.

User Interface 2 provides functionality for setting system operatingparameters, observing system operations, and controlling systemperformance. Typical embodiments range from a simple menu selection forinput with numerical output, to dynamic graphical display which changesbased on digital and analog output. The primary embodiment is agraphical user interface typically utilized for smart phones andcontent-rich portable computing devices. In this embodiment, UserInterface 2, Communications Module 4, and Microprocessor Controller 12are hosted on a single device.

In another embodiment, User Interface 2 is a separate device, or asoftware application residing on a general purpose computing platformand operating system. Communications Module 4 enables communicationsbetween User Interface 2, Microprocessor Controller 12, and devicesexternal to HBSC. External weather and climate data are provided to HBSCthrough Communications Module 4. Typical embodiments are based onindustry standard building automation protocols, including BACnet,Modbus, and Lon Works. Microprocessor Controller 12 hosts the softwarealgorithms containing system functionality. This compact embeddedmicroprocessor system accepts digital input from User Interface 2 anddigital/analog input from Sensor Inputs 6, and generates digital outputto User Interface 2, Communications Module 4, digital and analogcomponents within the Devices Controller 22.

To reduce development costs and increase manufacturing feasibility, opensource software and hardware is used, including MicroprocessorController 12, device operating system, shared libraries, and BACnetcommunications protocol. Open protocols are standardized communicationsand network layers published for use by any device manufacturer. HBSCarchitecture is designed to work in concert with commercial buildingautomation systems. In one embodiment, Microprocessor Controller 12processes sensor data, applies algorithms to extract control outputs,and communicates those outputs via standard architectures, such as aBACnet link in one embodiment. Software functionality includes a minimaldevice operating system, shared libraries, and support forindustry-standard communications. Microprocessor Controller 12 canoperate as a stand-alone controller or provide output to the buildingautomation system via BACnet, to execute algorithms for device control.The Physical Communications Layer is an industry standard, such as 100Base—T Ethernet between HBSC, the building automation system, and anetwork router. In one embodiment, the hardware consists of a series ofmicroprocessors based on advanced Reduced Instruction Set Computing(RISC) machine cores, which are comparable to hardware available inrecent smart phones and hosted using methods developed by the DOENational Renewable Energy Laboratory. In this embodiment, a modifiedLinux operating system is optimized for embedded applicationsprocessing.

SENSORS—Sensor Inputs 6 provide analog and digital input for systemcontrol. Control devices contain at least one member of the groupconsisting of sensor inputs for temperature, pressure, relativehumidity, air and fluid velocity, and real time energy use. From theseinputs, methods known in the art are used to calculate dew point, energyand thermal production (kWh and Btu's) and energy use by component andprocess. Control decisions use algorithms which provide the highestsystem energy efficiency as measured by energy produced divided byenergy used over a time period. In one embodiment of the devicecontrolling HBSC system as shown in FIG. 1, temperature sensors arelocated in:

-   Conditioned Space 10;-   Thermally-Conductive Structure 16;-   the outside air;-   the input and output of Radiant Mixing Device 14;-   Source Mixing Device One 86;-   Source Mixing Device Two 88;-   Thermal Storage One 46;-   Thermal Storage Two 80;-   Source 3-Way Control Valves One 56;-   Source 3-Way Control Valves Two 58;-   Bypass 3-Way Control Valves 74;-   Thermal Storage Source 3-Way Control Valves 78;-   Thermal Load 3-Way Control Valves 84;-   Hydronic Supply Fluid 38;-   Hydronic Return Fluid 40;-   Hydronic Coil Return Fluid 48;-   Hydronic Coil Supply Fluid 50;-   demand and source supply and return on Heat Pump 72, Process Heat    Exchanger 68, Heat Pump 72, and Source Heat Exchanger 76; and-   supply and return to the Ground Heat Exchanger One 64 and Ground    Heat Exchanger Two 66.

Fluid velocity sensors are located in:

-   Hydronic Load Circulator 52;-   Hydronic-to-Air Circulator 54;-   Source Side Circulator One 60;-   Source Side Circulator Two 62;-   Load Circulator 70; and-   Process Heat Circulator 90.

Air velocity sensors are located in:

-   the supply and return fans of Fresh Air Fan 30;-   Exhaust Air Fan 34;-   Conditioned Air 24, and-   Stale Exhaust Air 18.

Humidity and atmospheric pressure sensors are located in ConditionedSpace 10. Devices which consume power during system operation areequipped with watt/hr meters. These include circulators (Hydronic LoadCirculator 52, Hydronic-to-Air Circulator 54, Source Side Circulator One60, Source Side Circulator Two 62, Load Circulator 70, and Process HeatCirculator 90); fans (Fresh Air Fan 30, Exhaust Air Fan 34); and HeatPump 72. Using known methods, this sensor configuration is sufficient tocalculate component and system energy efficiency in real time, andcalculate dew point in real time in Conditioned Space 10 andThermally-Conductive Structure 16. This information is used by HBSCalgorithms to provide control outputs to digital and analog devices.System energy efficiency overrides component energy efficiency whenenergy savings is highest at the system level. The overall system powerusage is determined from sensors. The component actual power usage isdetermined from sensors, or component calculated power usage using thecomponent rated efficiencies (EER/COP) provided by the manufacturerusing one or more performance parameters.

Devices Controller 22 accepts Microprocessor Controller 12 output toaffect control of digital or analog devices including mixing (RadiantMixing Device 14, Source Mixing Device One 86, and Source Mixing DeviceTwo 88); 3-way valves (Source 3-Way Control Valves One 56, Source 3-WayControl Valves Two 58, Bypass 3-Way Control Valves 74, Thermal StorageSource 3-Way Control Valves 78, and Thermal Load 3-Way Control Valves84); Heat Pump 72; Hydronic Coil-to-Air Heat Exchanger 42, Fresh Air Fan30, and components which lack digital onboard input capabilities.Devices Controller 22 provides binary (on/off) control signals, orvariable control signals (such as a 01-10 volt signal).

User Interface 2, Communications Module 4, Microprocessor Controller 12,and Devices Controller 22 are able to implement the controls strategywhich optimizes system energy efficiency. The software and hardware ofthese four components have the flexibility to implement a wide varietyof known control strategies. These include set point control, setbackcontrol, reset control, low and high limit control, LEAD/LAG control,high/low signal select, and averaging control. The control logic isimplemented as (1) an open loop control in which decisions are basedonly on the model of how the system should operate; or (2) as a closedloop control in which the result of an output is fed back to thecontroller as an input. To simplify installation and commissioning, HBSCcontains preset algorithms known to produce the highest system energyefficiency. An example is modulating the Source Side Circulator One 60and Source Side Circulator Two 62 as a linear function to the compressorspeed of Heat Pump 72. All of these settings of system operatingparameters are stored in memory in Microprocessor Controller 12.

COOLING OPERATION—Conditioned Space 10 and Thermally-ConductiveStructure 16 are at a temperature above the desired comfort set pointtemperature in Conditioned Space 10. HBSC is programmed with stagedpriority cooling and ventilation set to multiple stages, e.g., Stage 1—Energy Transfer and Ventilation Device 32; Stage 2 —radiant floorcooling through Thermally-Conductive Structure 16; and Stage 3 —forcedair cooling through Hydronic Coil-to-Air Heat Exchanger 42.

If fresh air ventilation is required within Conditioned Space 10 or ifthe outdoor air temperature is lower than the desired comfort set pointin Conditioned Space 10, HBSC activates the Energy Transfer andVentilation Device 32 to circulate cool outside air in Conditioned Space10. If the outside air is cooler than Conditioned Space 10 by a presetoffset temperature and cooling demand is met within a preset timeperiod, Stage 1 cooling is the only means activated. If Stage 1 coolingdoes not meet cooling demand within a preset time period or to meetprogrammed response requirements such as a change in temperature overtime, Stage 2 cooling is activated.

Stage 2 cooling extracts heat from Conditioned Space 10 using theThermally-Conductive Structure 16. Based on sensor input fortemperature, relative humidity, and atmospheric pressure, MicroprocessorController 12 calculates the dew point of Thermally-Conductive Structure16 and Conditioned Space 10. Microprocessor Controller 12 adds an offsettemperature to the higher of these dew points, which determines MixedRadiant Supply Fluid 8. The sources for chilled fluid include ThermalStorage One 46, Ground Heat Exchanger One 64 and Ground Heat ExchangerTwo 66, or Process Heat Exchanger 68. In one embodiment, Process HeatExchanger 68 is eliminated and Ground Heat Exchanger One 64 and GroundHeat Exchanger Two 66 fluids are used directly to cool theThermally-Conductive Structure 16. Heat Pump 72 can be activated tochill Thermal Storage One 46 if no source is at or below the requiredMixed Radiant Supply Fluid 8 temperature. If either Ground HeatExchanger One 64 or Ground Heat Exchanger Two 66, or Process HeatExchanger 68 are at a lower temperature than the required Mixed RadiantSupply Fluid 8 temperature, HBSC activates Bypass 3-Way Control Valves74 to bypass Heat Pump 72, activates Thermal Storage Source 3-WayControl Valves 78 to Thermal Storage One 46 position, and activates LoadCirculator 70 and respective Source Side Circulator One 60, Source SideCirculator Two 62, or Process Heat Circulator 90 to chill ThermalStorage One 46. When Thermal Storage Temperature Sensor One 44 sensesthat Thermal Storage One 46 temperature is lower than the desired setpoint for the mixed radiant supply fluid, HBSC activates Thermal Load3-Way Control Valves 84 to Thermal Storage One 46 setting and activatesHydronic Load Circulator 52. Radiant Mixing Device 14 is modulated tomaintain the desired Mixed Radiant Supply Fluid 8 temperature. If thesource fluid maintains the set point temperature, the Stage 2 coolingcontinues until the comfort temperature in Conditioned Space 10 is met.If during Stage 2 cooling, HBSC determines that a chilled Mixed RadiantSupply Fluid 8 temperature cannot meet cooling demand, or that therequired Mixed Radiant Supply Fluid 8 temperature that meets coolingdemand is below the dew point, Stage 3 cooling is activated.

Stage 3 cooling requires Thermal Storage One 46 tank temperature to beless than dew point in order to condense moisture on the fan coil andaffect dehumidification of air passing through Hydronic Coil-to-Air HeatExchanger 42. Using the same logic finding a source in Stage 2 cooling,HBSC activates Stage 3 cooling of Thermal Storage One 46 based on thesource providing the highest cooling thermal output at the lowest energyinput. If Process Heat Exchanger 68 or Ground Heat Exchanger One64/Ground Heat Exchanger Two 66 fluids are at a higher temperature thanthe required Thermal Storage One 46 temperature, HBSC directs Bypass3-Way Control Valves 74 to the Heat Pump 72 position, selects the sourceheat exchanger fluid at the lowest temperature, and activates the lowestHeat Pump 72 compressor setting to meet the chilled water demand. Thissetting can be pre-programmed as an open loop control, or calculated inreal time using feedback from Thermal Storage Temperature Sensor One 44response over a set time period. As the temperature drops in ThermalStorage One 46, Radiant Mixing Device 14 modulates the mixing ofHydronic Return Fluid 40 to maintain Mixed Radiant Supply Fluid 8 abovethe set point above dew point.

When Heat Pump 72 cools Thermal Storage One 46 below the temperaturerequired for air coil condensation, HBSC activates Hydronic-to-AirCirculator 54 to circulate Hydronic Coil Supply Fluid 50. If the energytransfer and ventilation is not already operating, HBSC turns onHydronic-to-Air Circulator 54 to the lowest fan setting which providessufficient ventilation and maximum dehumidification across the fan coil.As Fresh Intake Air 28 passes through Hydronic Coil-to-Air HeatExchanger 42, the resultant Conditioned Air 24 will be cooled and haveless humidity than Fresh Air Supply 36. With continuous operation, thisprocess will lower the relative humidity and calculated dew point inConditioned Space 10. The lower dew point in Thermally-ConductiveStructure 16 will enable a lower Mixed Radiant Supply Fluid 8temperature making Thermally-Conductive Structure 16 more effective as acooling heat exchanger.

Using historic data, climate data, or real time weather data, thestaging and set points of these options can be adjusted to predict setpoints for optimal comfort, or stage processes for optimal system energyefficiency. HBSC incorporates thermal mass of Thermally-ConductiveStructure 16 by creating LEAD/LAG times for temperature response basedon structure.

In another embodiment, Heat Pump 72 can chill Thermal Storage One 46while rejecting heat to Thermal Storage Two 80 or Process Heat Exchanger68 without using Ground Heat Exchanger One 64 or Ground Heat ExchangerTwo 66. In low grade temperature applications such as pool heating whilecooling a chilling tower, the system energy efficiency is twice that ofa heat pump heating or chilling while operating with the ground heatexchanger.

HEATING OPERATION—It is known that radiant floor heating processes aremature art and condensation on Thermally-Conductive Structure 16 is nota consideration. HBSC provides innovations beyond current art toincrease user comfort, design flexibility, and energy efficiencyimprovements.

HBSC uses a reset curve to determine a set point to meet heat demand inConditioned Space 10. This set point is based on outside airtemperature, Conditioned Space 10 air temperature, Thermally-ConductiveStructure 16 temperature, and desired comfort set point. In oneembodiment, HBSC uses weather forecast data to modify set points forefficiency and comfort using known algorithms such as such aspre-cooling prior to forecast peak demand loads. Similar to coolingsequences, HBSC accepts temperature sensor inputs to determine highestsystem energy efficiency based on passive heat from Process HeatExchanger 68 or Ground Heat Exchanger One 64 or Ground Heat ExchangerTwo 66, or active heating using Heat Pump 72. If Heat Pump 72 is thesource of high grade heat, HBSC could select one or more Ground HeatExchanger One 64 or Ground Heat Exchanger Two 66 or Process HeatExchanger 68 as a source fluid providing the highest Heat Pump 72heating efficiency. Using known algorithms and Heat Pump 72 manufacturerperformance data, efficiency increases when providing hotter sourcewater in heating mode and cooler source water in cooling mode withinspecific operating ranges. This method may be overridden when systemenergy efficiency is higher at source temperatures different than thattemperature for highest Heat Pump 72 efficiency when considering allsystem components.

In one embodiment, Process Heat Exchanger 68 is a high temperature solarthermal array. HBSC would select this source for passive heating byactivating Source 3-Way Control Valves One 56 and Source 3-Way ControlValves Two 58 to position Process Heat Exchanger 68, activating Bypass3-way Control Valves 74 to bypass Heat Pump 72, and activating ThermalStorage Source 3-way Control Valves 78 to the Thermal Storage Two 80position. If the solar thermal production reduces Process Heat Exchanger68 temperature below the required Mixed Radiant Supply Fluid 8temperature, but at a temperature higher than the Ground Heat ExchangerOne 64 or Ground Heat Exchanger Two 66, Heat Pump 72 would be activatedin heating mode and operating against Process Heat Exchanger 68 as thesource.

If this source continued to drop in temperature below that of GroundHeat Exchanger One 64/Ground Heat Exchanger Two 66, HBSC would affectthe valve and pump positions to operate Heat Pump 72 in a conventionalconfiguration with the ground heat exchangers.

Ground Heat Exchanger One 64/Ground Heat Exchanger Two 66 may bemonolithic, or separate into one or more zones. The embodiment shown inFIG. 1 shows two separate ground heat exchanger zones. This number ofzones can be increased by adding a dedicated source circulator (such asSource Side Circulator One 60/Source Side Circulator Two 62) and sourcemixing device (such as Source Mixing Device One 86/Source Mixing DeviceTwo 88) to additional ground heat exchanger zones. These zones can serveas thermal energy storage for the overall system moving energy from theThermal Storage One 46/Thermal Storage Two 80) or Process Heat Exchanger68. The thermal storage can either be chilling or heating high thermalmass. In the case of Process Heat Exchanger 68 representing a solar hotwater thermal array, Ground Heat Exchanger One 64/Ground Heat ExchangerTwo 66 can store excess heat from the solar thermal system to address afuture thermal need. Similarly, heat extracted from Conditioned Space 10via Thermally-Conductive Structure 16 and rejected to Thermal StorageTwo 80, can be extracted from Thermal Storage Two 80 and sent to GroundHeat Exchanger One 64 or Ground Heat Exchanger Two 66.

The application of HBSC is not limited to radiant floor applications.Anywhere that the embodiment refers to Thermally-Conductive Structure16, another embodiment for the hydronic distribution is to a hydronicfan coil similar to the function of Hydronic Coil-to-Air Heat Exchanger42. In commercial buildings, the embodiment of the hydronic distributionto the conditioned space is to a thermally conductive structure, whichinvolves radiant low or high mass structures, hydronic fan coils, orvariable air velocity hydronic fan coils.

Control Algorithm Optimization Beyond the Current Art—HBSC implementsinnovative algorithms that reduce building energy use at a substantiallylower cost than the energy saved. One embodiment is hosted on a physicalmicroprocessor based on low-cost commodity hardware developed for thesmart phone industry.

HBSC energy savings potential increases substantially when advanced GHPequipment and high mass hydronic architecture are integrated in aholistic design. FIG. 2 illustrates controls potential to reduce energybased on equipment selection and distribution system, as compared to abaseline gas forced-air heating system with conventional outdoor directexchanger vapor compression refrigeration.

The major technology gaps overcome by HBSC include:

-   -   1. Implementing operating parameters for RFC and humidity        control for multiple climate zones, and algorithms which provide        the highest system energy efficiency for tracking dew point and        actively controlling humidity;    -   2. Meeting the functional requirements and metrics by        implementing the sequence of controls and software for the        proposed hydronic systems architecture; and    -   3. Deploying optimization algorithms for highest system energy        efficiency during GHP partial and full load conditions, for        Water-to-Water and Water-to-Air GHPs, equipped with single        stage, two-stage, and variable speed compressors, and the linear        control of fixed, multiple, and variable speed source        circulators.

These technology innovations are illustrated in FIG. 3. Thefunctionality defined by the shaded areas represents algorithms forpassive heating and cooling potential. HBSC algorithms use a conceptualmodel which implements a hydronic design providing interoperabilitybetween GHPs and alternative thermal heating and cooling sources.Traditional control architectures lack interoperability and innovation.Controls are typically designed to operate one device. In residentialapplications, a dedicated thermostat controls the furnace, a surfacemounted aqua stat controls the hot water heater, a switch controls thebath fan, etc. These controls are wired using industry standardleast-common-denominator bus connections for basic heat, cool, or fanwhich are not designed for the highest performance. One control unitdoes not know the existence of, or the capabilities of, another controlunit or equipment within the home or building. While commercialapplications may operate multiple devices, the controls logic andfeatures are similar to residential systems. As equipment or newfunctions are added, the overall system resembles a jigsaw puzzle ofincreasing complexity where potential energy improvements are limited tothe interoperability (or lack thereof) with existing infrastructure. Innew construction involving commercial buildings with advanced features,dedicated controls contractors must write custom code to provide thelinks between disparate equipment, sensors, and controls. In general,these DDC programmers lack the knowledge to optimize component andsystem efficiencies.

By applying client-server computing architectures, such as shown in FIG.4, to building controls, HBSC overcomes these interoperabilitylimitations. HBSC is based on a model representing the potential heatingand cooling and ventilation processes available to meet userrequirements. A common Client-Server Architecture 400 providesinteroperability to legacy and new equipment. Rather than requiring newequipment to fit into the puzzle created by the existing infrastructure,the new equipment must comply with a common systems architecturestandard. The complexity of the system is reduced to common applicationprogramming interfaces. Quite simply, any Client (a control) 402/404/406should communicate to any Server (HVAC equipment) 408. As proven withinformation technology (IT) systems, Client-Server Architectures 400 arepowerful.

One HBSC embodiment is a building controls architecture based on BACnet,a national and international standard proven in commercial applicationsand readily available. One market barrier to BACnet controls is the highcost of BACnet-compatible hardware processors. The lowest cost controlsplatform is one which has the largest worldwide market share. Oneembodiment to reduce the hardware cost of this processor is to host iton a RISC-based smart phone platform.

BACnet-compatible algorithms are ported to a commodity hardwaremicroprocessor platform developed to serve the smart phone industry. Asshown below in FIG. 5, a HBSC device will serve as an applicationcontroller within a larger network, or as a low cost control forstandalone applications.

HBSC software implements process control for a functional model of ageneric building heating, cooling, and hot water system. The model hasfunctions found in traditional buildings and advanced features thatimplement controls technology unavailable today. The basic functionalityuses best practices algorithms known in the art for the control oftraditional equipment for the production of hot water, chilled water,and ventilation equipment. Integrated systems capabilities make HBSCinnovative. While using known algorithms, the implementation is uniquewith advanced hydronic features unavailable in controls today.Capabilities include dew point tracking with humidity control, whichenables radiant floor cooling implementations, and direct use of solarthermal fluids for heating, or ground heat exchanger fluids for passivecooling. For the control of legacy and new GHP equipment, HBSC controlsthe source circulators in a linear relationship to compressor demand tooptimize system performance.

HBSC has the collective potential to increase the Seasonal PerformanceFactor for the Heating System (SPF_(HS)) up to 30% over traditional GHPdesigns using conventional controls. When installed with high massradiant cooling, the system energy efficiency increases to 40% overconventional forced air GHP systems. These gains are derived from theeffectiveness of the radiant floor infrastructure and the lowercondenser temperatures within the GHP. RFC systems require twice thetubing density (six inches on-center spacing) of radiant floor heatingsystems. As compared to heating, RFC requires a higher volume of heattransfer fluid (usually water) which increases thermal mass and systemlag time (time period for fluid to complete one circuit through thedistribution system), while decreasing hydronic circulation flow ratewhich reduces circulator energy. Embedded in a structural concrete slabor lightweight concrete topping, a high mass radiant floor configuredfor cooling is a highly efficient heat transfer medium. The tubingdensity required for a RFC heat exchanger increases the heat transfercoefficient and reduces the mean temperature difference. With the sameinlet temperature and an increased flow rate through the GHP, therequired mean temperature differential can be maintained with a lowercondensation temperature. For the GHP condenser in heating mode, thismeans a lower average temperature level and thus a lower condensingpressure and reduced compressor work. Designing the hydronic heatingsystem for the supply temperature of 90 degrees F. at the Design OutdoorAir Temperature (DOAT), instead of the more common 125 degrees F., willincrease the SPF_(HS) by approximately 40% (using the estimate that COPincreases by 2% for each 1 degree K. of lowered condensationtemperature).

Since the thermal mass of the radiant floor will affect the cyclicbehavior of the heat pump and temperature level of the system, it hasthe effect of lowering condensation temperatures even further.Traditionally, W-A GHPs with Electronically Commutated Motor (ECM) fanshave a higher ARI COP rating than W-W GHPs. The SPF_(HS) for low massintermittent systems operation is 3% higher than high mass systems. Thisis due to the lower supply temperatures during compressor operation.However, low mass systems increase compressor cycling and contribute touser thermal discomfort caused by rapid changes in air temperaturesbetween cycles. High thermal mass increases the system lag time. Anexample of low thermal mass radiant structures is PEX tubing which isattached to a low mass structure such as floor sheathing or wallpaneling. A high mass structure involves embedding the PEX tubing (orany other type of appropriate piping) in concrete, light weightconcrete, gypsum, or related high density material which creates lagtime when heating or cooling due to the mass of the material.

A GHP equipped with a single stage compressor operating at full capacityand supplying a radiant hydronic system with a ten minute lag timeincreases SPF_(HS) by 5% versus a radiator system with no lag time. Thisis shown in FIG. 6.

The SPF_(HS) increases with increasing lag time because the averagesupply temperature is reduced during the compressor on-time. The plateauat the beginning of the cycle depicted by the solid line is due to lagtime. The increase in SPF_(HS) is optimal when a single stage W-W GHP issized at a capacity which is 70-80% of the peak building demand at theDOAT.

While radiant heating algorithms are mature, the RFC optimization andcontrol approach implemented in HBSC represents a significantadvancement in the state of the art. HBSC is unique in the comprehensiveand discrete control of an integrated system used in the process modeland containing radiant floor cooling with dynamic dew point tracking andactive humidity control, dual process heating and cooling sources,ventilation using a hydronic coil in line with energy recovery, andsegmented ground heat exchangers to utilize alternative energy sourcesand optimize GHP and system performance. The innovative control enablesdeployment of this functionality as stand-alone capabilities, or as partof an integrated systems design as described in the first embodiment.

Hydronic Building Systems Control—Functionality And Benefits

1. Enable Radiant Floor Cooling With Humidity Control Functionality—Peakgrid demand is driven by building cooling loads. Reducing peak coolingloads reduces grid energy use. RFC reduces cooling system energy by17%-42% depending on climate zone, operates at higher distributionefficiencies than forced air, enables personal comfort space zoning,limits terrorist intrusion vulnerabilities of forced-air HVAC systems,and inherently eliminates the health risk from fatal infectious diseasescaused by gram negative, aerobic bacteria (such as Legionella). RFC hasthe capacity to remove 12-14 Btu/h/ft² sensible gain and 25-32 Btu/h/ft²of radiant heat gain in spaces with direct solar exposure, such as largeglass atriums. Using radiant roll-out mat installation methods,cross-linked polyethylene (PEX) tubing embedded in new constructionconcrete slabs is one-half the first cost of forced air ductwork.Existing buildings with installed high mass radiant floor heating can beupgraded to RFC at minimal cost. To avoid condensation in RFCapplications, dew point sensing controls are required. RFC controls areavailable to control set cooling water temperature based on dew point,though these controls lack the functionality to actively controlhumidity. HBSC extends the art by providing this capability.

The primary function is to control cooling in a thermally-conductivestructure, such as RFC or chilled beams. Radiant heating algorithms willuse conventional methods. Zone sensors provide temperature, atmosphericpressure (or, the atmospheric pressure is accounted for bypre-programming in the algorithms, eliminating the need for atmosphericpressure sensors), and relative humidity data to determine a system dewpoint, and to set a supply water temperature which prevents condensationwithin the structure. When indoor humidity is low, wet bulb gain isnegligible. With RFC, latent heat is removed by an air conditioning andventilation system which incorporates air velocity sensing. In dryclimates, a separate air conditioning system may not be required, as achilled W-A coil used in conjunction with the VAV or ERV/HRV can providelimited latent heat extraction and dehumidification. In theseapplications, the control must provide chilled water below dew point tothe W-A coil for dehumidification, while mixing RFC water to an offsettemperature above dew point for use in the high massthermally-conductive structure.

Radiant cooling systems are particularly effective at reducing directsolar heat gain on indoor floor surfaces. This is particularly relevantto passive solar homes where the design intentionally provides fullshade in the summer and full sun in the winter. The high thermal mass ofradiant heated floors exposed to direct solar heating tends to overheatthe conditioned space. In winter months with mild outdoor airtemperatures and a very efficient building envelope, high performancehomes tend to overheat in mid-day with low sun angles. A radiant floorcooling system has the ability to directly extract infrared heat gainsfrom the thermally conductive structure to prevent overheating in thisscenario. Heat extracted for cooling is utilized in the integratedsystem to provide immediate heating or stored for future use.

The efficiency of radiant cooling is limited by latent heat loads. FIG.7 depicts an estimate of RFC potential within U.S. climate zones.

2. Implement Dual Process Heating Cooling Applications—Moving heat isusually more efficient than converting fuel or electricity to generateheat or cooling. Heat pumps inherently “move heat.” The COP of a GHPdoubles when the heat pump moves heat directly from a chilling source toa heating source without a ground heat exchanger. High mass hydronicsystems operate at moderate temperatures, thus increasing equipmentefficiency and providing an opportunity for direct use of passiveheating or cooling with thermal storage. HBSC algorithms implementmodel-based passive strategies including night cooling, direct use ofground-coupled hydronic loops bypassing the chiller, segmenting theground source heat exchanger to serve as a heat sink, ice storage, andnight fluid or pre-cooling functionality. HBSC provides interoperabilitybetween traditional air cooling and dehumidification equipment, hydronicchillers/boilers, direct digital and analog to GHPs with innovativefeatures, and accepts sensors for temperature, pressure, humidity, andair velocity and water flow. The controller selects an active or passivesource based on set point heat and cooling source temperatures to meetbuilding loads. It can operate as a standalone controller forresidential applications, or serve as an industry standards-compliantsub-system controller for complex residential and commercialapplications.

3. Segmented Ground Source Heat Exchanger—The GHEX is often oversizedfor cooling loads when designed for heating-dominated buildings orclimates. With an integrated solar thermal system, this excess GHEXcapacity can reduce costs and improve the GHP COP. The solar factor ofthermal hot water systems is limited by storage capacity, which is oftensized based on the thermal capacity of the array. Solar thermalcollectors are one-half the costs of the required storage tanks sized tothe array capacity. Therefore, the installed cost per Btu of capacityfor a solar thermal array is substantially reduced if the solar array isexpanded without increasing thermal tank storage capacity. A split orsegmented GHEX makes this possible for heating dominated annual buildingloads. Consider the example for a GHP sized for ten GHEX loops or wellsduring winter heating operation. During summer operation, the GHEX meetsthe smaller cooling load using only six loops or wells, with theremaining four loops or wells available for thermal storage. The solarthermal array can be increased by the capacity provided by these fourloops or wells. These loops or wells are “superheated” when compared tothe stable ground temperature. When the GHP enters heating mode, COPincreases as a result of the higher entering water temperature from theGHEX using all ten loops or wells. For a period of time during thetransition from cooling to heating season, the hydronic radiant floorapplications may directly use GHEX water in the heated loops or wells.HBSC will compare the radiant demand set point temperature to the GHEXloops or well temperature and solar thermal supply temperature to selecta direct energy source, or the need to operate the GHP compressor tomeet demand, which is higher (in heating) or lower (in cooling) to meetthe space conditioning requirements.

With system-wide sensing and digital control of an advanced GHP, HBSCwill operate the GHP to provide the highest system COP/EER. HBSCcontroller is operable to command the following actions:

-   -   1. Direct use of the solar thermal fluid (bypassing the GHEX);    -   2. Direct use of GHEX fluid;    -   3. Engage the GHP to heat/cool the load side fluid to set point        based on an outdoor reset; or    -   4. Perform a combination of these functions.

The proposed integrated HBSC represents a significant advance overexisting controls which are plagued by incomplete functionality, highcost, complex and proprietary installation requirements, and a failureto recognize advanced capabilities of GHPs. HBSC delivers an affordableand interoperable control based on existing commercial standards, andreduces installation cost, complexity, and serviceability of the controlsystem.

Related Research or R&D—Thermodynamics is not a new science. A patent ofparticular relevance to radiant floor cooling was issued in 1993 toGaliyano (U.S. Pat. No. 5,261,251) which disclosed a hydronic coolingand heating system through a slab with an in-ground heat exchanger andcompressor. U.S. Pat. No. 7,234,314 discloses methods for geothermalheating and cooling with solar heating. Dehumidification using an ERV isdisclosed in U.S. Pat. No. 7,845,185. Dr. Roy Crawford has a patentpending for humidity control for air conditioning systems (U.S. PatentPublication No. 2007/0261422 A1). Control algorithms have beenresearched since the mid-20t^(h) century. Today, this basic science isused in residential, commercial, and industrial buildings worldwide.Work in Sweden by Karlsson and Fahlén are just a few of many that haveshown ground source heat pumps can be optimized in hydronic heating andcooling applications. The literature is replete with current research inthis area.

Likewise, software programmable microprocessors with open standardsinteroperability such as BACnet have been developed for decades. Whiledifferent in application, the science of enterprise control of heatingand cooling systems is not new or particularly complex. The uniquecombination of these elements into a single low cost control system isinnovative and unique. There are undoubtedly hundreds of patents forcontrols involving radiant hydronic heating and cooling systems,variable speed devices, solar thermal storage, and latent heatextraction.

With more advanced control algorithms, system efficiencies utilizing W-WGHPs can be increased substantially. By focusing mainly on incrementalenhancements to existing systems, controls manufacturers have avoidedinnovative HVAC products and designs which promise to deliver thehighest return on investment when balancing first costs with energysavings. Examples include the control of two-stage and variable speedwater-water GHPs and multi-speed and variable speed flow center pumps.There has been no demand for an optimized control for integratedhydronic systems with water-water GHPs, since no U.S. GHP manufactureroffers VS technology in W-W heat pumps. In Europe, VS W-W heat pumps areequipped with internal controls for heating only applications. Controlsmanufacturers have not addressed the need for enterprise control asgeothermal heat pumps represent less than ½% of the HVAC control marketof which W-W units in hydronic applications constitute a minisculemarket segment.

European hydronic system configurations and modeling methods are themost compelling, and specifically research funded by the Swedish EnergyAgency (SEA) involving W-W GHPs equipped with VS compressors, electronicexpansion valves, and variable frequency drive circulators in hydronicheating applications.

The European Heat Pump Association has reported that more than 127,000heat pumps were installed in Sweden in 2011 making Sweden the largestmarket in Europe. While hydronic heating with radiators is the prevalentdistribution system, new homes utilize in-floor heating. According tothe SEA, the heat pumps installed will supply 22.5 Terawatt Hours (TWh)of capacity. Of this, 15 TWh is free energy from the ground representing10% of all energy supplied to Swedish buildings. Research which isrelevant to this innovation was funded by the SEA and carried out at SPTechnical Research Institute of Sweden and Chalmers University ofTechnology, in collaboration with Wilo, Grundfos, Carrier, Uponor, andothers. The scope of work was “to investigate the potential forincreased system energy efficiency of heat pumps by applyingvariable-speed capacity control to compressors, pumps and fans, as wellas an overall strategy for on-line optimization of the operation,” withthe core focus on GHPs connected to hydronic heating. The SEA studyresults are consistent with proposed HBSC functions implementingGHP-centric hydronic systems in the United States, including:

-   -   1. System design and control can positively impact system energy        efficiency more than individual component improvements (GHP,        pumps, compressors, and fans). When evaluating VS and        intermittent GHP operation, it is important to consider the        transient behavior of the heating system (not just steady state        conditions);    -   2. The use of efficient circulators is of primary importance for        GHPs equipped with VS compressors;    -   3. Source circulator capacity control can be implemented using        simple algorithms approaching optimal control. These algorithms        can be external to the circulator, as many internal (on-line)        state-of-the-art controls need improvement for optimal        efficiency;    -   4. The SPF_(HS) is the appropriate metric for the energy        efficient design of an integrated GHP hydronic heating system;    -   5. With optimal control, SPF_(HS) can be improved 30% over        conventional methods; and    -   6. Heat pump EER and COP are poor predictors of overall system        heating and cooling system performance.

Ground source heat pump source side flow requirements are the keyexternal determinant affecting GHP efficiency. Serial hydronic systemsdesigns for conventional boiler systems are not appropriate for GHPapplications, since source side flow rate is not optimized fordistribution loop flow. This concept is shown in FIG. 8. The connectionof the GHP to the hydronic system assumes a primary/secondary pipingconfiguration as shown on the left in FIG. 8. The design incorporates aparallel connection which differs from a typical boiler heating systempiped in series to the distribution circuit shown on the right in FIG.8.

This method decouples the heat pump demand circuit from the hydronicdistribution, so that loop flows are optimal for the respectiveapplication. The most energy efficient flow rate for the hydronic loopoccurs at the lowest flow rate that will meet building demand. Lowerflow rates during heating are possible when the system is designed forthe increased PEX tubing density required for RFC operation. Theslightly higher materials cost are offset by the benefits incurred:lower operating costs, reduced noise and erosion, and lower headpressure. The hydronic loop (Circulator 1 in FIG. 8) flow rate should behigher than the demand loop (Circulator 2) to insure mixing occurs onthe supply side A, instead of the return side B. This configurationensures GHP efficiency based on optimum entering water temperature.

The ideal flow in the demand loop is dependent on the GHP configurationand capacity, related to the building load. Contrary to conventionalwisdom, the optimal design may not optimize the COP; rather, it shouldbe based on the SPF_(HS). COP is the performance ratio of heat suppliedto the demand loop compared to the work consumed in a steady state by anelectric compression heat pump at a given set of temperature conditions.SPF is the ratio of the heat energy delivered (Btu's) and the totalenergy supplied (watt/hr) over a season. While the system heating metricSPF_(HS) is illustrative, cooling system performance would utilize asimilar metric such as SPF_(CS). SPF differs from COP in that boundaryparameters can be established for the Heat Pump (SPF_(HP)), Heat PumpSystem including pumps or fans (SPF_(HPS)), or the Heating System(SPF_(HS)), GHP, pumps, fans, and supplement heating. SPF accounts forintermittent or partial load GHP operation, varying operatingtemperatures, and energy expended for ancillary equipment operation. COPcan be misleading on predicting actual energy savings. For instance, aVS GHP delivers better performance at partial load conditions with an11% increase in COP. A GHP equipped with a single stage compressor has a14-19% higher SPF_(HS) after considering the energy losses of theVariable Frequency Drive (VFD) and circulation pumps operating at fullspeed under partial load conditions. HBSC establishes a demand loop flowrate to optimize SPF_(HS), yet as a secondary function to the sourceside circulator.

The dominant control parameter to establish optimal SPF_(HS) or SPF_(CS)for fixed and VS GHPs is source circulator flow rate. This controlparameter outweighs the effect of any other parameter depicted in FIG. 9outlining the system boundary conditions for a typical GHP. The demandcircuit input data are load return water temperature (t_(wi)), theevaporator temperature, evaporator superheat, required demand capacity,and the temperature differential between t₅ and t_(wi) across the heatexchanger. The source circuit input data include the source enteringwater temperature (EWT, or t_(bi)—brine in), the temperature of therefrigerant leaving the condenser, the condensing pressure, and theevaporator superheat. Controlling the source side flow set point (groundloop flow center) is the key determinant to GHP efficiency. Varyingdemand side circulator flow from 60% to 100% capacity affects actual COPby only 1% as compared to the optimal COP. In contrast, setting thesource circulator speed as a linear function of the compressor speed canimprove the SPF_(HS) as much as 20% for single or two-stage W-W GHPs, orVS GHPs without on-board flow center circulator control.

Although the subject matter has been described in language specific tostructural features and/or methodological acts, it is to be understoodthat the subject matter defined in the appended claims is notnecessarily limited to the specific features or acts described above.Rather, the specific features and acts described above are disclosed asexample forms of implementing the claims. It will be understood by thoseskilled in the art that many changes in construction and circuitry andwidely differing embodiments and applications will suggest themselveswithout departing from the scope of the disclosed subject matter.

What is claimed is:
 1. An apparatus comprising: at least twowater-source heat pumps fluidly connected to at least one ground heatexchanger; a first source circulator having variable speed and fluidlyconnected to a source heat exchanger on a source side of each of the atleast two water-source heat pumps, wherein the first source circulatorcirculates a source fluid through the at least two water-source heatpumps and the at least one ground heat exchanger; a plurality of sensorsthat send a plurality of sensor inputs to a microprocessor controller,the plurality of sensors selected from the group consisting of at leasttwo of: at least one source fluid entering water temperature sensor; atleast one source fluid leaving water temperature sensor; at least oneload fluid entering water temperature sensor; at least one load fluidleaving water temperature sensor; at least one temperature sensor; atleast one pressure sensor; at least one fluid velocity sensor; at leastone power sensor; and at least one real time energy use sensor; a memorycoupled to and readable by the microprocessor controller and storingtherein a plurality of instructions that, when executed by themicroprocessor controller, causes the microprocessor controller to:receive at least one of: a heating demand; and a cooling demand;calculate a source circulator speed to maintain a flow rate of thesource fluid through the at least two water-source heat pumps; to meetat least one of: the heating demand; and the cooling demand; in responseto processing at least one of: at least one temperature data; at leastone pressure data; at least one fluid velocity data; at least one powerdata; and at least one real time energy use data; to achieve at leastone of: maintain a leaving water temperature; maintain a temperaturedifferential between the leaving water temperature and an entering watertemperature; at least one energy efficiency; and at least one comfortbenefit; and send a first source circulator control signal to the firstsource circulator causing the first source circulator to operate at thesource circulator speed.
 2. The apparatus according to claim 1 furthercomprising: the at least two water-source heat pumps are selected fromthe group consisting of at least one of: a water-air geothermal heatpump; a water-water geothermal heat pump; a water-air water-source heatpump; and a water-water water-source heat pump.
 3. The apparatusaccording to claim 1 further comprising: substituting the at least oneground heat exchanger for at least one of: the at least one ground heatexchanger; and a source process heat exchanger; wherein the sourceprocess heat exchanger is selected from the group consisting of: athermal storage, a boiler, a chiller, a cooling tower, a water-to-waterheat pump, an air-to-water heat pump, a solar thermal array, a combinedheat and power unit, and an absorption chiller.
 4. The apparatusaccording to claim 1 further comprising: substituting the at least oneground heat exchanger for at least one of: the at least one ground heatexchanger; and direct use at least one second source fluid wherein theat least one second source fluid is comprised of at least one of: afluid from ground water a fluid from a body of water; and a fluid from asolar thermal array.
 5. The apparatus according to claim 1 furthercomprising: the first source circulator is selected from the groupconsisting of at least one of: the first source circulator; the firstsource circulator and a second source circulator having one stage; thesecond source circulator having one stage and a third source circulatorhaving one stage; and a fourth source circulator having two stages;wherein the first source circulator control signal comprises at leastone of: the first source circulator control signal sent to the firstsource circulator; a second source circulator control signal sent to thesecond source circulator; a third source circulator control signal sentto the third source circulator; and a fourth source circulator controlsignal sent to the fourth source circulator; to maintain the flow rateof the source fluid.
 6. The apparatus according to claim 1 wherein theplurality of sensors is selected from the group consisting of at leastfive of: the at least one source fluid entering water temperaturesensor; the at least one source fluid leaving water temperature sensor;the at least one load fluid entering water temperature sensor; the atleast one load fluid leaving water temperature sensor; at least oneevaporator temperature sensor; at least one evaporator pressure sensor;at least one condenser temperature sensor; at least one condenserpressure sensor; at least one compressor discharge temperature sensor;the at least one temperature sensor; the at least one pressure sensor;the at least one fluid velocity sensor; the at least one power sensor;and the at least one real time energy use sensor.
 7. The apparatusaccording to claim 6 wherein at least one of: the at least one sourcefluid entering water temperature sensor; the at least one source fluidleaving water temperature sensor; the at least one load fluid enteringwater temperature sensor; and the at least one load fluid leaving watertemperature sensor; are configured to measure the temperature of atleast one of: an entering temperature to the source heat exchanger ofthe at least two water-source heat pumps; a leaving temperature from thesource heat exchanger of the at least two water-source heat pumps; anentering temperature to the at least one ground heat exchanger; and aleaving temperature from the at least one ground heat exchanger.
 8. Theapparatus according to claim 1 wherein the at least one fluid velocitysensor is selected from the group consisting of at least one of: adirect mass flow measurement; an indirect mass flow measurement; adirect volumetric flow measurement; and an indirect volumetric flowmeasurement.
 9. The apparatus according to claim 1 wherein the at leastone fluid velocity sensor is at least one flow rate switch.
 10. Theapparatus according to claim 1 further comprising: the microprocessorcontroller increases at least one of: a preselected source circulatorspeed; and the source circulator speed; upon receiving in real time theat least one fluid velocity data indicating at least one source fluidflow rate is less than a minimum fluid flow rate.
 11. The apparatusaccording to claim 1 further comprising: the microprocessor controllerincreases the source circulator speed upon receiving in real time atleast one of: the at least one fluid velocity data; and a source fluidtemperature; indicating at least one of: a source fluid flow rate isless than a minimum fluid flow rate; and the source fluid temperature isbelow a minimum source fluid temperature.
 12. The apparatus according toclaim 1 wherein the at least one fluid velocity sensor is integral to atleast one of: the first source circulator; a second source circulator; athird source circulator; and a fourth source circulator.
 13. Theapparatus according to claim 1 wherein at least one water temperaturesensor is integral to at least one of: the first source circulator; asecond source circulator; a third source circulator; and a fourth sourcecirculator.
 14. The apparatus according to claim 1 wherein themicroprocessor controller calculates the flow rate of the source fluidin response to receiving a data selected from the group consisting of atleast one of: a minimum flow rate; a maximum flow rate; an intermediateflow rate; a minimum temperature; a maximum temperature; a differentialtemperature, and a differential pressure.
 15. The apparatus according toclaim 1 wherein the microprocessor controller calculates the flow rateof the source fluid using a demand data considering a thermal mass of aconditioned space.
 16. The apparatus according to claim 1 wherein the atleast two water-source heat pumps comprise at least one of: the sourceheat exchanger is a condenser and the load heat exchanger is anevaporator; and the source heat exchanger is the evaporator and the loadheat exchanger is the condenser.
 17. The apparatus according to claim 1further comprising: the at least two water-source heat pumps areconfigured with a reversing valve to achieve at least one of: heat aload heat exchanger; and cool a load heat exchanger.
 18. The apparatusaccording to claim 1 wherein the at least one energy efficiency is anefficiency of the apparatus measured by an energy produced divided by anenergy used over a time period.
 19. The apparatus according to claim 1wherein the at least one energy efficiency is an efficiency of theapparatus calculated using an operating cost.
 20. The apparatusaccording to claim 1 further comprising: the at least two water-sourceheat pumps are fluidly connected to at least one of: at least one sourceentering water mixing valve; and at least one source entering water flowcontrol valve; the plurality of instructions comprises at least oneentering water control valve algorithm that, when executed by themicroprocessor controller, and in response to receiving and processingat least one of: the heating demand; and the cooling demand; causes themicroprocessor controller to send at least one entering watertemperature flow control signal to at least one of: the at least onesource entering water mixing valve; and the at least one source enteringwater flow control valve; to modulate at least one of: a source enteringwater temperature; and a source entering water flow rate; in order toachieve at least one of: the at least one energy efficiency; and the atleast one comfort benefit.
 21. The apparatus according to claim 1wherein the plurality of instructions comprises at least one thermalmass predictive control algorithm that, when executed by themicroprocessor controller, and in response to receiving and processingat least one performance data of a rate of change in a temperature overtime for at least one of: a thermally conductive structure; and aconditioned space; causes the microprocessor controller to determine anoptimal delay time before sending at least one of: at least one firstcontrol signal to the first source circulator to operate at the sourcecirculator speed; and at least one second control signal to a first loadcirculator to operate at a load circulator speed; to achieve at leastone of: the at least one energy efficiency; and the at least one comfortbenefit.
 22. The apparatus according to claim 1 further comprising: adevices controller that receives a plurality of digital signals from themicroprocessor controller; wherein the devices controller sends aplurality of control signals; and a plurality of devices receives theplurality of control signals.
 23. The apparatus according to claim 1wherein the plurality of instructions comprises a plurality of setpoints that are received by the microprocessor controller and can beadjusted.
 24. The apparatus according to claim 1 wherein the apparatusfurther comprises at least one of: a user interface; a communicationsmodule; and a wireless interface for communicating with at least onemobile device.
 25. The apparatus according to claim 24 wherein thecommunications module further comprises at least one of: a BACnet; aModbus; and a LonWorks data communications protocol.
 26. The apparatusaccording to claim 1 wherein the apparatus is configured to process atleast one of: a historical data; a climate data; and a real time weatherdata; received from at least one of: a website through a communicationsmodule; the historical data; an outdoor sensor; a sensor which measuresat least one outdoor weather condition; to achieve at least one of: theat least one energy efficiency; and the at least one comfort benefit.27. The apparatus according to claim 26 wherein at least one outdoorreset heating control algorithm causes the microprocessor controller to:calculate a reset temperature of a load fluid based on an outdoortemperature; and send at least one of: a load circulator speed controlsignal to a load circulator; and the first source circulator controlsignal to the source circulator; to maintain the reset temperature at alowest temperature to meet the demand.
 28. The apparatus according toclaim 26 wherein at least one outdoor reset cooling control algorithmcauses the microprocessor controller to: calculate a reset temperatureof a load fluid based on an outdoor temperature; and send at least oneof: a load circulator speed control signal to a load circulator; and thefirst source circulator control signal to the source circulator; tomaintain the reset temperature at a highest temperature to meet thedemand.
 29. The apparatus according to claim 26 wherein: the pluralityof instructions comprises at least one outdoor reset control algorithmthat, when executed by the microprocessor controller, and in response toreceiving and processing at least two of: at least one cooling set pointtemperature; at least one heating set point temperature; the historicaldata; the climate data; and the real time weather data; causes themicroprocessor controller to modify at least one of: the at least onecooling set point temperature; the at least one heating set pointtemperature; and a set point humidity; to meet in a conditioned space atleast one of: the cooling demand; the heating demand; the at least oneenergy efficiency; and the at least one comfort benefit.
 30. Theapparatus according to claim 1 further comprising at least one of: theplurality of instructions that, when executed by the microprocessorcontroller is executed by least one of: the microprocessor controller adedicated controller on a device; and the microprocessor controller incommunication with the dedicated controller on the device; and at leastone control signal that, when executed by the microprocessor controlleris sent by at least one of: the microprocessor controller the dedicatedcontroller on the device; and the microprocessor controller incommunication with the dedicated controller on the device.
 31. Theapparatus according to claim 30 wherein the device is selected from thegroup consisting of at least one of: a component within thewater-to-water heat pump; a component within a fan coil unit; acompressor controller; a source circulator; a load circulator; a devicescontroller; and a communications module.
 32. An apparatus comprising: anair-to-water heat pump configured with a variable speed compressor tomeet a demand, wherein the variable speed compressor has multiplestages; a first load circulator having variable speed and fluidlyconnected to a load heat exchanger on a load side of the air-to-waterheat pump wherein the first load circulator circulates a load fluidthrough the load heat exchanger; a plurality of sensors that send aplurality of sensor inputs to a microprocessor controller, the pluralityof sensors selected from the group consisting of at least three of: atleast one source fluid entering water temperature sensor; at least onesource fluid leaving water temperature sensor; at least one load fluidentering water temperature sensor; at least one load fluid leaving watertemperature sensor; at least one evaporator temperature sensor; at leastone condenser temperature sensor; at least one temperature sensor; atleast one pressure sensor; at least one fluid velocity sensor; at leastone power sensor; and at least one real time energy use sensor; a memorycoupled to and readable by the microprocessor controller and storingtherein a plurality of instructions that, when executed by themicroprocessor controller, causes the microprocessor controller to:receive at least one of: a heating demand; and a cooling demand;calculate at a first compressor speed and a load circulator speed tomaintain a flow rate of the load fluid: to meet at least one of: theheating demand; and the cooling demand; in response to processing atleast two of: at least one temperature data; at least one pressure data;at least one fluid velocity data; at least one power data; and at leastone real time energy use data; to achieve at least one of: maintain aleaving water temperature; maintain a temperature differential betweenthe leaving water temperature and an entering water temperature;maintain a preselected first compressor speed; at least one energyefficiency; and at least one comfort benefit; and execute at least twoof: send a first compressor speed control signal to the variable speedcompressor causing the variable speed compressor to operate at the firstcompressor speed; and send a first load circulator control signal to thefirst load circulator causing the first load circulator to operate atthe load circulator speed.
 33. The apparatus according to claim 32further comprising: the variable speed compressor is selected from thegroup consisting of at least one of: the variable speed compressor; asecond compressor having one stage and a third compressor having onestage; and a fourth compressor having two stages; wherein themicroprocessor controller calculates at least two of: the firstcompressor speed; a second compressor speed; a third compressor speed; afourth compressor speed; and the load circulator speed to maintain aflow rate of the source fluid; and the first compressor speed controlsignal sent by the microprocessor controller comprises at least one of:the first compressor speed control signal sent to the variable speedcompressor; a second compressor speed control signal sent to the secondcompressor; a third compressor speed control signal sent to the thirdcompressor; and a fourth compressor speed control signal sent to thefourth compressor.
 34. The apparatus according to claim 32 furthercomprising: the first load circulator is selected from the groupconsisting of at least one of: the first load circulator; the first loadcirculator and a second load circulator having one stage; the secondload circulator having one stage and a third load circulator having onestage; and a fourth load circulator having two stages; wherein the firstload circulator control signal comprises at least one of: the first loadcirculator control signal sent to the first load circulator; a secondload circulator control signal sent to the second load circulator; athird load circulator control signal sent to the third load circulator;and a fourth load circulator control signal sent to the fourth loadcirculator; to maintain the flow rate of the load fluid.
 35. Theapparatus according to claim 32 wherein the plurality of sensors isselected from the group consisting of at least five of: the at least onesource fluid entering water temperature sensor; the at least one sourcefluid leaving water temperature sensor; the at least one load fluidentering water temperature sensor; the at least one load fluid leavingwater temperature sensor; the at least one evaporator temperaturesensor; at least one evaporator pressure sensor; the at least onecondenser temperature sensor; at least one condenser pressure sensor; atleast one compressor discharge temperature sensor; the at least onetemperature sensor; the at least one pressure sensor; the at least onefluid velocity sensor; the at least one power sensor; and the at leastone real time energy use sensor.
 36. The apparatus according to claim 32wherein the at least one fluid velocity sensor is selected from thegroup consisting of at least one of: a direct mass flow measurement; anindirect mass flow measurement; a direct volumetric flow measurement;and an indirect volumetric flow measurement.
 37. The apparatus accordingto claim 32 wherein the at least one fluid velocity sensor is at leastone flow rate switch.
 38. The apparatus according to claim 32 furthercomprising: the microprocessor controller increases at least one of: apreselected load circulator speed; and the load circulator speed; uponreceiving in real time the at least one fluid velocity data indicating aload fluid flow rate is less than a minimum fluid flow rate.
 39. Theapparatus according to claim 32 wherein the at least one fluid velocitysensor is integral to at least one of: the first load circulator; asecond load circulator; a third load circulator; and a fourth loadcirculator.
 40. The apparatus according to claim 32 wherein at least onewater temperature sensor is integral to at least one of: the first loadcirculator; a second load circulator; a third load circulator; and afourth load circulator.
 41. The apparatus according to claim 32 whereinthe microprocessor controller calculates the flow rate of the load fluidin response to receiving a data selected from the group consisting of atleast one of: a minimum flow rate; a maximum flow rate; an intermediateflow rate; a minimum temperature; a maximum temperature; a differentialtemperature, and a differential pressure.
 42. The apparatus according toclaim 32 wherein the microprocessor controller calculates the flow rateof the load fluid using a demand data considering a thermal mass of aconditioned space.
 43. The apparatus according to claim 32 wherein theair-to-water heat pump comprises at least one of: the source heatexchanger is a condenser and the load heat exchanger is an evaporator;and the source heat exchanger is the evaporator and the load heatexchanger is the condenser.
 44. The apparatus according to claim 32further comprising: the air-to-water heat pump is configured with areversing valve to achieve at least one of: heat the load fluid; andcool the load fluid.
 45. The apparatus according to claim 44 wherein themicroprocessor controller defaults to cool the load fluid.
 46. Theapparatus according to claim 32 wherein the at least one energyefficiency is an efficiency of the apparatus measured by an energyproduced divided by an energy used over a time period.
 47. The apparatusaccording to claim 32 wherein the at least one energy efficiency is anefficiency of the apparatus calculated using an operating cost.
 48. Theapparatus according to claim 32 further comprising: the air-to-waterheat pump is fluidly connected to at least one of: at least one sourceentering water mixing valve; and at least one source entering water flowcontrol valve; the plurality of instructions comprises at least oneentering water control valve algorithm that, when executed by themicroprocessor controller, and in response to receiving and processingat least one of: the heating demand; and the cooling demand; causes themicroprocessor controller to send at least one entering watertemperature flow control signal to at least one of: the at least onesource entering water mixing valve; and the at least one source enteringwater flow control valve; to modulate at least one of: a source enteringwater temperature; and a source entering water flow rate; in order toachieve at least one of: the at least one energy efficiency; and the atleast one comfort benefit.
 49. The apparatus according to claim 32further comprising: the load heat exchanger fluidly connected to athermally conductive structure in thermal communication with aconditioned space wherein the first load circulator circulates the loadfluid in the thermally conductive structure; and the plurality ofinstructions comprises at least one hydronic supply fluid flow ratealgorithm that, when executed by the microprocessor controller, and inresponse to receiving and processing at least one of: the heatingdemand; and the cooling demand; causes the microprocessor controller tocalculate at least one of: a hydronic supply fluid flow rate of the loadfluid; and the first compressor speed; to meet in the conditioned spaceat least one of: the heating demand; the cooling demand; the at leastone energy efficiency; and the at least one comfort benefit; and send atleast one of: at least one hydronic supply fluid flow control signal tothe first load circulator causing the load fluid to circulate at thehydronic supply fluid flow rate; and the first compressor speed controlsignal to the variable speed compressor causing the air-to-water heatpump to maintain a temperature of the load fluid; to meet in theconditioned space at least one of: the cooling demand; the heatingdemand; the at least one energy efficiency; and the at least one comfortbenefit.
 50. The apparatus according to claim 49 wherein the pluralityof instructions comprises at least one thermal mass predictive controlalgorithm that, when executed by the microprocessor controller, and inresponse to receiving and processing at least one performance data of arate of change in a temperature over time for at least one of: thethermally conductive structure; and the conditioned space; causes themicroprocessor controller to determine an optimal delay time beforesending at least one control signal to at least one of: the variablespeed compressor causing the variable speed compressor to operate at thefirst compressor speed; the first source circulator to operate at thesource circulator speed; and the first load circulator causing the firstload circulator to operate at the load circulator speed. to achieve atleast one of: the at least one energy efficiency; and the at least onecomfort benefit.
 51. The apparatus according to claim 32 furthercomprising: the load heat exchanger fluidly connected to at least onefan coil unit comprising a fan and a hydronic coil-to-air heat exchangerfluidly connected to the load heat exchanger and circulating aconditioned air in a conditioned space wherein the first load circulatorcirculates the load fluid in the hydronic coil-to-air heat exchanger;and the plurality of instructions comprises at least one hydronic coilsupply fluid flow rate algorithm that, when executed by themicroprocessor controller, and in response to receiving and processingat least one of: the heating demand; and the cooling demand; causes themicroprocessor controller to calculate at least one of: the at least onehydronic coil supply fluid flow rate of the load fluid; and the firstcompressor speed; to meet in the conditioned space at least one of: theheating demand; the cooling demand; the at least one energy efficiency;and the at least one comfort benefit; and send at least one of: at leastone hydronic coil supply fluid flow control signal to the first loadcirculator causing the load fluid to circulate at the at least onehydronic coil supply fluid flow rate; and the first compressor speedcontrol signal to the variable speed compressor causing the air-to-waterheat pump to maintain a temperature of the load fluid; to meet in theconditioned space at least one of: the cooling demand; the heatingdemand; the at least one energy efficiency; and the at least one comfortbenefit.
 52. The apparatus according to claim 32 further comprising: adevices controller that receives a plurality of digital signals from themicroprocessor controller; wherein the devices controller sends aplurality of control signals; and a plurality of devices receives theplurality of control signals.
 53. The apparatus according to claim 32wherein the plurality of instructions comprises a plurality of setpoints that are received by the microprocessor controller and can beadjusted.
 54. The apparatus according to claim 32 wherein the apparatusfurther comprises at least one of: a user interface; a communicationsmodule; and a wireless interface for communicating with at least onemobile device.
 55. The apparatus according to claim 54 wherein thecommunications module further comprises at least one of: a BACnet; aModbus; and a LonWorks data communications protocol.
 56. The apparatusaccording to claim 32 wherein the apparatus is configured to process atleast one of: a historical data; a climate data; and a real time weatherdata; received from at least one of: a website through a communicationsmodule; the historical data; an outdoor sensor; and a sensor whichmeasures at least one outdoor weather condition; to achieve at least oneof: the at least one energy efficiency; and the at least one comfortbenefit.
 57. The apparatus according to claim 56 wherein: the pluralityof instructions comprises at least one outdoor reset heating controlalgorithm that, when executed by the microprocessor controller, and inresponse to receiving and processing at least two of: the heatingdemand; the historical data; the climate data; and the real time weatherdata; causes the microprocessor controller to execute at least one of:send the first load circulator control signal to the first loadcirculator causing the first load circulator to circulate the load fluidthrough the load heat exchanger; and send the first compressor speedcontrol signal to the variable speed compressor causing the air-to-waterheat pump to maintain a temperature of the load fluid only when: theheating demand call is present; and at least one of: the historicaldata; the climate data; and the real time weather data; indicates anoutside air temperature is below a set point temperature.
 58. Theapparatus according to claim 57 wherein the at least one outdoor resetheating control algorithm causes the microprocessor controller to:calculate a reset temperature of the load fluid based on an outdoortemperature; and send at least one of: the first load circulator controlsignal; and the first compressor speed control signal; to maintain thereset temperature at a lowest temperature to meet the demand.
 59. Theapparatus according to claim 57 wherein the at least one outdoor resetcooling control algorithm causes the microprocessor controller to:calculate a reset temperature of the load fluid based on an outdoortemperature; and send at least one of: the first load circulator controlsignal; and the first compressor speed control signal; to maintain thereset temperature at a highest temperature to meet the demand.
 60. Theapparatus according to claim 56 wherein: the plurality of instructionscomprises at least one outdoor reset control algorithm that, whenexecuted by the microprocessor controller, and in response to receivingand processing at least two of: at least one cooling set pointtemperature; at least one heating set point temperature; the historicaldata; the climate data; and the real time weather data; causes themicroprocessor controller to modify at least one of: the at least onecooling set point temperature; the at least one heating set pointtemperature; and the set point humidity; to meet in a conditioned spaceat least one of: the cooling demand; the heating demand; the at leastone energy efficiency; and the at least one comfort benefit.
 61. Theapparatus according to claim 32 further comprising at least one of: theplurality of instructions that, when executed by the microprocessorcontroller is executed by least one of: the microprocessor controller adedicated controller on a device; and the microprocessor controller incommunication with the dedicated controller on the device; and at leastone control signal that, when executed by the microprocessor controlleris sent by least one of: the microprocessor controller the dedicatedcontroller on the device; and the microprocessor controller incommunication with the dedicated controller on the device.
 62. Theapparatus according to claim 61 wherein the device is selected from thegroup consisting of at least one of: a component within the air-to-waterheat pump; a component within a fan coil unit; a compressor controller;a load circulator; a devices controller; and a communications module.